U.S. patent application number 17/350516 was filed with the patent office on 2022-02-24 for scroll compressor.
The applicant listed for this patent is LG Electronics Inc.. Invention is credited to Jungsun CHOI, Kangwook LEE, Kyungho LEE.
Application Number | 20220056910 17/350516 |
Document ID | / |
Family ID | |
Filed Date | 2022-02-24 |
United States Patent
Application |
20220056910 |
Kind Code |
A1 |
LEE; Kyungho ; et
al. |
February 24, 2022 |
SCROLL COMPRESSOR
Abstract
A scroll compressor according to the present disclosure includes
a fixed scroll, an orbiting scroll forming first and compression
chambers with the fixed scroll, first and second compression
chamber oil supply holes formed through the orbiting scroll to
communicate with the first compression chamber and the second
compression chamber, respectively, wherein when a section in which
the first compression chamber oil supply hole is opened toward the
first compression chamber is a first oil supply section and a
section in which the second compression chamber oil supply hole is
opened toward the second compression chamber, a non-overlap section
between the first oil supply section and the second oil supply
section may be longer than an overlap section between the first oil
supply section and the second oil supply section, so as to prevent
communication between the first and second compression chambers,
thereby suppressing leakage between the compression chambers.
Inventors: |
LEE; Kyungho; (Seoul,
KR) ; CHOI; Jungsun; (Seoul, KR) ; LEE;
Kangwook; (Seoul, KR) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
LG Electronics Inc. |
Seoul |
|
KR |
|
|
Appl. No.: |
17/350516 |
Filed: |
June 17, 2021 |
International
Class: |
F04C 29/02 20060101
F04C029/02; F04C 18/02 20060101 F04C018/02 |
Foreign Application Data
Date |
Code |
Application Number |
Aug 20, 2020 |
KR |
10-2020-0104856 |
Claims
1. A scroll compressor comprising: a casing; a driving motor
provided in the casing; a fixed scroll disposed at a side of the
driving motor, the fixed scroll including a fixed end plate and a
fixed wrap positioned at the fixed end plate; an orbiting scroll
including (i) an orbiting end plate facing the fixed end plate, and
(ii) an orbiting wrap positioned at the orbiting end plate and
configured to be engaged with the fixed wrap to define a first
compression chamber and a second compression chamber; a first
compression chamber oil supply hole that is defined at the orbiting
end plate and configured to be in fluid communication with the
first compression chamber; and a second compression chamber oil
supply hole that is defined at the orbiting end plate and
configured to be in fluid communication with the second compression
chamber, wherein the first compression chamber oil supply hole is
configured to be opened toward the first compression chamber during
a first oil supply stage, wherein the second compression chamber
oil supply hole is configured to be opened toward the second
compression chamber during a second oil supply stage, and wherein
the first oil supply stage overlaps the second oil supply stage
during a first period of time, and does not overlap the second oil
supply stage during a second period of time, the first period of
time being longer than the first period of time.
2. The scroll compressor of claim 1, wherein the first compression
chamber oil supply hole includes a first outlet that is in fluid
communication with the first compression chamber, wherein the
second compression chamber oil supply hole includes a second outlet
that is in fluid communication with the second compression chamber,
and wherein the first outlet and the second outlet are located at
portions of the orbiting end plate that restrict the first oil
supply stage from overlapping the second oil supply stage.
3. The scroll compressor of claim 1, wherein the first compression
chamber is defined between an inner circumferential surface of the
fixed wrap and an outer circumferential surface of the orbiting
wrap, wherein the second compression chamber is defined between an
outer circumferential surface of the fixed wrap and an inner
circumferential surface of the orbiting wrap, wherein the first
compression chamber oil supply hole includes a first outlet that is
spaced apart by a first distance from an outer circumferential
surface of an outermost orbiting wrap, and wherein the second
compression chamber oil supply hole includes a second outlet that
is spaced apart by a second distance from an inner circumferential
surface of the outermost orbiting wrap.
4. The scroll compressor of claim 3, wherein the first distance is
greater than or equal to the second distance.
5. The scroll compressor of claim 3, wherein the first distance is
greater than or equal to a first value obtained by subtracting an
inner diameter of the first outlet of the first compression chamber
oil supply hole from a first wrap thickness of the orbiting wrap
adjacent to the first outlet of the first compression chamber oil
supply hole.
6. The scroll compressor of claim 5, wherein the second distance is
greater than or equal to a second value obtained by subtracting an
inner diameter of the second outlet of the second compression
chamber oil supply hole from a second wrap thickness of the
orbiting wrap adjacent to the second outlet of the second
compression chamber oil supply hole.
7. The scroll compressor of claim 3, wherein the first outlet of
the first compression chamber oil supply hole is spaced apart by a
first distance from the outer circumferential surface of the
outermost orbiting wrap, the first distance being equal to or
greater than an inner diameter of the first outlet of the first
compression chamber oil supply hole, and wherein the second outlet
of the second compression chamber oil supply hole is spaced apart
by a second distance from the inner circumferential surface of the
outermost orbiting wrap, the second distance being equal to or
greater than an inner diameter of the second outlet of the second
compression chamber oil supply hole.
8. The scroll compressor of claim 1, wherein the second oil supply
stage starts at an end of the first oil supply stage, and the first
oil supply stage starts at a preset interval from an end of the
second oil supply stage.
9. The scroll compressor of claim 8, wherein the preset interval
corresponds to a crank angle of greater than 0.degree. and smaller
than or equal to 30.degree..
10. The scroll compressor of claim 2, wherein the first outlet of
the first compression chamber oil supply hole is defined at a first
position that permits the first compression chamber oil supply hole
to fluidly communicate with the first compression chamber based on
a suction in the first compression chamber being completed.
11. The scroll compressor of claim 10, wherein the second outlet of
the second compression chamber oil supply hole is defined at a
second position that permits the second compression chamber oil
supply hole to fluidly communicate with the second compression
chamber based on a suction in the second compression chamber being
competed.
12. The scroll compressor of claim 11, wherein the first outlet of
the first compression chamber oil supply hole is configured, based
on a crank angle being 0.degree. at a position that an outer
circumferential surface of a suction end of the orbiting wrap
contacts an inner circumferential surface of the fixed wrap, to be
defined in a first range that permits first pockets to overlap each
other, the first pockets defining the first compression chamber
respectively at crank angles of 0.degree., 90.degree., and
180.degree..
13. The scroll compressor of claim 12, wherein the second outlet of
the second compression chamber oil supply hole is configured, based
on the crank angle being 0.degree. at the position that the outer
circumferential surface of the suction end of the orbiting wrap
contacts the inner circumferential surface of the fixed wrap, to be
defined in a second range that permits second pockets to overlap
each other, the second pockets defining the second compression
chamber respectively at crank angles of 180.degree., 260.degree.,
and 320.degree..
14. The scroll compressor of claim 1, wherein the second
compression chamber oil supply hole includes a second outlet
configured to be blocked with respect to the second compression
chamber in the first oil supply stage, and wherein the first
compression chamber oil supply hole includes a first outlet
configured to be blocked with respect to the first compression
chamber in the second oil supply stage.
15. The scroll compressor of claim 14, wherein the first outlet of
the first compression chamber oil supply hole is configured to be
defined in a crank angle range of 0.degree. to 90.degree. in a
first pressure ratio stage, and wherein the second outlet of the
second compression chamber oil supply hole is configured to be
defined in a crank angle range of 180.degree. to 260.degree. in the
first pressure ratio stage.
16. The scroll compressor of claim 15, wherein the first outlet of
the first compression chamber oil supply hole is configured to be
defined in a crank angle range of 90.degree. to 180.degree. in a
second pressure ratio stage, and wherein the second outlet of the
second compression chamber oil supply hole is configured to be
defined in a crank angle range of 260.degree. to 320.degree. in the
second pressure ratio stage, the second pressure ratio stage being
greater than the first pressure ratio stage.
17. The scroll compressor of claim 16, wherein the first outlet of
the first compression chamber oil supply hole is configured to be
defined in a crank angle range of 180.degree. to 250.degree. in a
third pressure ratio stage, and wherein the second outlet of the
second compression chamber oil supply hole is configured to be
defined in a crank angle range of 320.degree. to 380.degree. in the
third pressure ratio stage, the third pressure ratio stage being
greater than the second pressure ratio stage.
18. The scroll compressor of claim 1, wherein the orbiting scroll
includes an oil accommodating portion that is in fluid
communication with an inner space of the casing, and wherein the
first compression chamber oil supply hole and the second
compression chamber oil supply hole are in fluid communication with
the oil accommodating portion.
19. The scroll compressor of claim 18, wherein the orbiting scroll
defines a rotating shaft coupling portion through the orbiting
scroll in an axial direction, the rotating shaft coupling portion
configured to receive a rotating shaft, the scroll compressor
further comprising an eccentric portion bearing that is fitted with
an inner circumferential surface of the rotating shaft coupling
portion, and wherein the eccentric portion bearing is shorter in
length than the rotating shaft coupling portion, and wherein the
oil accommodating portion is defined at an annular shape between an
end of the eccentric portion bearing and the inner circumferential
surface of the rotating shaft coupling portion.
20. The scroll compressor of claim 17, further comprising: a first
pressure reducing member positioned in the first compression
chamber oil supply hole, and a second pressure reducing member
positioned in the second compression chamber oil supply hole,
wherein an outer diameter of the first pressure reducing member is
smaller than an inner diameter of the first compression chamber oil
supply hole, and wherein an outer diameter of the second pressure
reducing member is smaller than an inner diameter of the second
compression chamber oil supply hole.
Description
CROSS-REFERENCE TO RELATED APPLICATION
[0001] Pursuant to 35 U.S.C. .sctn. 119(a), this application claims
the benefit of the earlier filing date and the right of priority to
Korean Patent Application No. 10-2020-0104856, filed on Aug. 20,
2020, the contents of which is incorporated by reference herein in
its entirety.
TECHNICAL FIELD
[0002] This implementation relates to a scroll compressor, and more
particularly, an oil supply structure of a scroll compressor.
BACKGROUND
[0003] A scroll compressor is a compressor forming a compression
chamber including a suction chamber, an intermediate pressure
chamber, and a discharge chamber between both scrolls while the
plurality of scrolls is an engaged state. Such a scroll compressor
may obtain a relatively high compression ratio and stable torque by
smooth connection of suction, compression, and discharge strokes of
refrigerant, as compared with other types of compressors.
Therefore, the scroll compressors are widely used for compressing
refrigerant in air conditioners or the like.
[0004] Scroll compressors may be classified into a top-compression
type and a bottom-compression type according to a position of a
compression unit relative to a motor unit. The top-compression type
is a compressor in which the compression unit is disposed above the
motor unit, and the bottom-compression type is a compressor in
which the compression unit is disposed below the motor unit.
[0005] In the top-compression type, since the compression unit is
located far from a lower space of a casing, oil stored in the lower
space of the casing is difficult to be moved to the compression
unit. On the other hand, in the bottom-compression type, since the
compression unit is located close to the lower space of the casing,
the oil stored in the lower space of the casing can be easily moved
to the compression unit. An implementation according to the present
disclosure will illustrate a bottom-compression type scroll
compressor. Therefore, hereinafter, a scroll compressor may be
defined as a bottom-compression type scroll compressor unless
otherwise specified.
[0006] The scroll compressor is provided with an oil supply portion
for guiding oil stored in the lower space of the casing to the
compression unit. The oil supply portion may supply oil using an
oil pump or using differential pressure. An oil supplying method
using the differential pressure can eliminate a component such as
an oil pump, thereby reducing a fabricating cost and effectively
supplying oil to the compression unit.
[0007] Some scroll compressors include an oil supply structure
using differential pressure. The oil supply structure in these
scroll compressors includes oil supply holes formed through a fixed
scroll to guide oil, which has been guided to an intermediate
pressure chamber, to a compression chamber. The oil supply holes
are formed to communicate with a first compression chamber formed
between an inner surface of a fixed wrap and an outer surface of an
orbiting wrap, and a second compression chamber formed between an
outer surface of the fixed wrap and an inner surface of the
orbiting wrap, respectively.
[0008] The oil supply hole communicating with the first compression
chamber may be defined as a first oil supply hole and the oil
supply hole communicating with the second compression chamber may
be defined as a second oil supply hole. The first oil supply hole
and the second oil supply hole are respectively formed at positions
where they are open before a suction completion time point of each
compression chamber. As the oil supply holes individually
communicate with the first compression chamber and the second
compression chamber, smooth oil supply to both compression chambers
can be expected even during a low-pressure ratio operation.
[0009] However, if the first oil supply hole communicating with the
first compression chamber and the second oil supply hole
communicating with the second compression chamber are provided, a
section in which the first oil supply hole and the second oil
supply hole communicate with each other may be generated during an
operation of the compressor. In the section where the first oil
supply hole and the second oil supply hole communicate with each
other, a part of refrigerant which is compressed in a compression
chamber where pressure is high may flow back into a compression
chamber where pressure is low due to such pressure difference
between the first compression chamber and the second compression
chamber. As a result, compression loss may occur due to leakage
between the compression chambers. This may often occur in an
operation of a low-pressure ratio which is less than 1.3.
SUMMARY
[0010] One aspect of the present disclosure is to provide a scroll
compressor, capable of suppressing compression loss in a first
compression chamber formed between an inner surface of a fixed wrap
and an outer surface of an orbiting wrap, and a second compression
chamber formed between an outer surface of the fixed wrap and an
inner surface of the orbiting wrap.
[0011] Another aspect of the present disclosure is to provide a
scroll compressor, capable of suppressing refrigerant compressed in
a high-pressure compression chamber from flowing back toward a
low-pressure compression chamber through an oil supply passage
while oil supply passages individually communicate with a first
compression chamber and a second compression chamber.
[0012] Still another aspect of the present disclosure is to provide
a scroll compressor, capable of preventing an oil supply passage
communicating with a first compression chamber and an oil supply
passage communicating with a second compression chamber from being
simultaneously open to the respective compression chambers based on
a crank angle, or minimizing a simultaneous open time.
[0013] Still another aspect of the present disclosure is to provide
a scroll compressor, capable of preventing a first compression
chamber and a second compression chamber from communicating with
each other through an oil supply passage while oil is smoothly
supplied to the first compression chamber and the second
compression chamber during a low-pressure ratio operation.
[0014] In order to achieve these and other advantages and in
accordance with the purpose of this specification, particular
implementations of the present disclosure provide a scroll
compressor that includes a casing, a driving motor provided in the
casing, a fixed scroll, an orbiting scroll, and first and second
compression chamber oil supply holes. The fixed scroll is disposed
at a side of the driving motor and includes a fixed end plate and a
fixed wrap positioned at the fixed end plate. The orbiting scroll
includes an orbiting end plate facing the fixed end plate, and an
orbiting wrap positioned at the orbiting end plate and configured
to be engaged with the fixed wrap to define a first compression
chamber and a second compression chamber. The first compression
chamber oil supply hole is defined at the orbiting end plate and
configured to be in fluid communication with the first compression
chamber. The second compression chamber oil supply hole is defined
at the orbiting end plate and configured to be in fluid
communication with the second compression chamber. The first
compression chamber oil supply hole is configured to be opened
toward the first compression chamber during a first oil supply
stage. The second compression chamber oil supply hole is configured
to be opened toward the second compression chamber during a second
oil supply stage. The first oil supply stage overlaps the second
oil supply stage during a first period of time, and does not
overlap the second oil supply stage during a second period of time.
The first period of time is longer than the first period of
time.
[0015] In some implementations, the scroll compressor can
optionally include one or more of the following features. The first
compression chamber oil supply hole may include a first outlet that
is in fluid communication with the first compression chamber. The
second compression chamber oil supply hole may include a second
outlet that is in fluid communication with the second compression
chamber. The first outlet and the second outlet may be located at
portions of the orbiting end plate that restrict the first oil
supply stage from overlapping the second oil supply stage. The
first compression chamber may be defined between an inner
circumferential surface of the fixed wrap and an outer
circumferential surface of the orbiting wrap. The second
compression chamber may be defined between an outer circumferential
surface of the fixed wrap and an inner circumferential surface of
the orbiting wrap. The first compression chamber oil supply hole
may include a first outlet that is spaced apart by a first distance
from an outer circumferential surface of an outermost orbiting
wrap. The second compression chamber oil supply hole may include a
second outlet that is spaced apart by a second distance from an
inner circumferential surface of the outermost orbiting wrap. The
first distance may be greater than or equal to the second distance.
The first distance may be greater than or equal to a first value
obtained by subtracting an inner diameter of the first outlet of
the first compression chamber oil supply hole from a first wrap
thickness of the orbiting wrap adjacent to the first outlet of the
first compression chamber oil supply hole. The second distance may
be greater than or equal to a second value obtained by subtracting
an inner diameter of the second outlet of the second compression
chamber oil supply hole from a second wrap thickness of the
orbiting wrap adjacent to the second outlet of the second
compression chamber oil supply hole. The first outlet of the first
compression chamber oil supply hole may be spaced apart by a first
distance from the outer circumferential surface of the outermost
orbiting wrap. The first distance may be equal to or greater than
an inner diameter of the first outlet of the first compression
chamber oil supply hole. The second outlet of the second
compression chamber oil supply hole may be spaced apart by a second
distance from the inner circumferential surface of the outermost
orbiting wrap. The second distance may be equal to or greater than
an inner diameter of the second outlet of the second compression
chamber oil supply hole. The second oil supply stage may start at
an end of the first oil supply stage, and the first oil supply
stage may start at a preset interval from an end of the second oil
supply stage. The preset interval may correspond to a crank angle
of greater than 0.degree. and smaller than or equal to 30.degree..
The first outlet of the first compression chamber oil supply hole
may be defined at a first position that permits the first
compression chamber oil supply hole to fluidly communicate with the
first compression chamber based on a suction in the first
compression chamber being completed. The second outlet of the
second compression chamber oil supply hole may be defined at a
second position that permits the second compression chamber oil
supply hole to fluidly communicate with the second compression
chamber based on a suction in the second compression chamber being
competed. The first outlet of the first compression chamber oil
supply hole may be configured, based on a crank angle being
0.degree. at a position that an outer circumferential surface of a
suction end of the orbiting wrap contacts an inner circumferential
surface of the fixed wrap, to be defined in a first range that
permits first pockets to overlap each other. The first pockets may
define the first compression chamber respectively at crank angles
of 0.degree., 90.degree., and 180.degree.. The second outlet of the
second compression chamber oil supply hole may be configured, based
on the crank angle being 0.degree. at the position that the outer
circumferential surface of the suction end of the orbiting wrap
contacts the inner circumferential surface of the fixed wrap, to be
defined in a second range that permits second pockets to overlap
each other. The second pockets may define the second compression
chamber respectively at crank angles of 180.degree., 260.degree.,
and 320.degree.. The second compression chamber oil supply hole may
include a second outlet configured to be blocked with respect to
the second compression chamber in the first oil supply stage. The
first compression chamber oil supply hole may include a first
outlet configured to be blocked with respect to the first
compression chamber in the second oil supply stage. The first
outlet of the first compression chamber oil supply hole may be
configured to be defined in a crank angle range of 0.degree. to
90.degree. in a first pressure ratio stage. The second outlet of
the second compression chamber oil supply hole may be configured to
be defined in a crank angle range of 180.degree. to 260.degree. in
the first pressure ratio stage. The first outlet of the first
compression chamber oil supply hole may be configured to be defined
in a crank angle range of 90.degree. to 180.degree. in a second
pressure ratio stage. The second outlet of the second compression
chamber oil supply hole may be configured to be defined in a crank
angle range of 260.degree. to 320.degree. in the second pressure
ratio stage. The second pressure ratio stage may be greater than
the first pressure ratio stage. The first outlet of the first
compression chamber oil supply hole may be configured to be defined
in a crank angle range of 180.degree. to 250.degree. in a third
pressure ratio stage. The second outlet of the second compression
chamber oil supply hole may be configured to be defined in a crank
angle range of 320.degree. to 380.degree. in the third pressure
ratio stage. The third pressure ratio stage may be greater than the
second pressure ratio stage. The orbiting scroll may include an oil
accommodating portion that is in fluid communication with an inner
space of the casing. The first compression chamber oil supply hole
and the second compression chamber oil supply hole may be in fluid
communication with the oil accommodating portion. The orbiting
scroll may define a rotating shaft coupling portion through the
orbiting scroll in an axial direction. The rotating shaft coupling
portion may be configured to receive a rotating shaft. The scroll
compressor may include an eccentric portion bearing that is fitted
with an inner circumferential surface of the rotating shaft
coupling portion. The eccentric portion bearing may be shorter in
length than the rotating shaft coupling portion. The oil
accommodating portion may be defined at an annular shape between an
end of the eccentric portion bearing and the inner circumferential
surface of the rotating shaft coupling portion. The scroll
compressor may include a first pressure reducing member positioned
in the first compression chamber oil supply hole, and a second
pressure reducing member positioned in the second compression
chamber oil supply hole. An outer diameter of the first pressure
reducing member may be smaller than an inner diameter of the first
compression chamber oil supply hole. An outer diameter of the
second pressure reducing member may be smaller than an inner
diameter of the second compression chamber oil supply hole.
[0016] In order to achieve these and other advantages and in
accordance with the purpose of this specification, as embodied and
broadly described herein, there is provided a scroll compressor, in
which a first crank angle range is out of a second crank angle
range under assumption that a crank angle range in which a first
compression chamber oil supply hole is opened with respect to a
first compression chamber is the first crank angle range and a
crank angle range in which a second compression chamber oil supply
hole is opened with respect to a second compression chamber is the
second crank angle range. Accordingly, the first crank angle range
and the second crank angle range do not overlap each other, which
may prevent the first compression chamber and the second
compression chamber from communicating with each other, thereby
suppressing leakage between the compression chambers.
[0017] Here, an interval between the first crank angle range and
the second crank angle range may be formed to be smaller than or
equal to 10.degree. based on a crank angle. This may result in
minimizing a section in which oil is not supplied and thus reducing
friction loss as much as possible.
[0018] In addition, in order to achieve those aspects and other
advantages of the present disclosure, there is provided a scroll
compressor, including a casing, a driving motor provided in an
inner space of the casing, a fixed scroll disposed at one side of
the driving motor and provided with a fixed end plate and a fixed
wrap formed on one side surface of the fixed end plate, an orbiting
scroll provided with an orbiting end plate facing the fixed end
plate, and an orbiting wrap formed on one side surface of the
orbiting end plate and engaged with the fixed wrap to form a first
compression chamber and a second compression chamber, and first and
second compression chamber oil supply holes formed through the
orbiting end plate to communicate with the first compression
chamber and the second compression chamber, respectively.
Accordingly, oil can be supplied to the first compression chamber
and the second compression chamber almost without interruption,
thereby increasing reliability of the compressor.
[0019] For example, a section in which the first oil supply section
and the second oil supply section do not overlap each other may be
longer than a section in which the first oil supply section and the
second oil supply section overlap each other. This may result in
minimizing the communication between the first compression chamber
and the second compression chamber through the first compression
chamber oil supply hole and the second compression chamber oil
supply hole.
[0020] Specifically, an outlet of the first compression chamber oil
supply hole communicating with the first compression chamber and an
outlet of the second compression chamber oil supply hole
communicating with the second compression chamber may be formed at
positions where the first oil supply section and the second oil
supply section do not overlap each other. This may result in
suppressing leakage between the first compression chamber and the
second compression chamber through the first compression chamber
oil supply hole and the second compression chamber oil supply
hole.
[0021] Here, the first compression chamber may be formed between an
inner circumferential surface of the fixed wrap and an outer
circumferential surface of the orbiting wrap, and the second
compression chamber may be formed between an outer circumferential
surface of the fixed wrap and an inner circumferential surface of
the orbiting wrap. An outlet of the first compression chamber oil
supply hole may be formed at a position spaced apart by a first
interval from an outer circumferential surface of an outermost
orbiting wrap, and an outlet of the second compression chamber oil
supply hole may be formed at a position spaced apart by a second
interval from an inner circumferential surface of the outermost
orbiting wrap. With the configuration, even during an operation of
a low pressure ratio of less than 1.3, in an oil supply section for
the first compression chamber and an oil supply section for the
second compression chamber, a first oil supply section in which the
first compression chamber oil supply hole is opened toward the
first compression chamber may not overlap a second oil supply
section in which the second compression chamber oil supply hole is
opened toward the second compression chamber, thereby enhancing
compression efficiency.
[0022] Here, the first interval may be greater than or equal to the
second interval. Accordingly, the outlet of the first compression
chamber oil supply hole and the outlet of the second compression
chamber oil supply hole can be formed at positions where the first
oil supply section and the second oil supply section do not overlap
each other.
[0023] In addition, the first interval may be formed at a position
equal to or greater than a value obtained by subtracting an inner
diameter of the outlet of the first compression chamber oil supply
hole from a wrap thickness of the orbiting wrap adjacent to the
outlet of the first compression chamber oil supply hole. The second
interval may be formed at a position equal to or greater than a
value obtained by subtracting an inner diameter of the outlet of
the second compression chamber oil supply hole from a wrap
thickness of the orbiting wrap adjacent to the outlet of the second
compression chamber oil supply hole. This may result in optimizing
positions of the first compression chamber oil supply hole and the
second compression chamber oil supply hole so that the first oil
supply section and the second oil supply section do not overlap
each other.
[0024] Here, the outlet of the first compression chamber oil supply
hole may be formed at a position spaced apart from the outer
circumferential surface of the outermost orbiting wrap by an inner
diameter of the outlet of the first compression chamber oil supply
hole or farther, and the outlet of the second compression chamber
oil supply hole may be formed at a position spaced apart from the
inner circumferential surface of the outermost orbiting wrap by an
inner diameter of the outlet of the second compression chamber oil
supply hole or farther.
[0025] The second oil supply section may start continuously from an
end of the first oil supply section, and the first oil supply
section may start at a preset interval from an end of the second
oil supply section.
[0026] An interval between the start of the first oil supply
section and the end of the second oil supply section may be greater
than 0.degree. and smaller than or equal to 30.degree. based on a
crank angle. Accordingly, a non-oil supply section can be minimized
even without an overlap between the first oil supply section and
the second oil supply section, thereby reducing friction loss of
the compressor.
[0027] The outlet of the first compression chamber oil supply hole
may be formed at a position where the first compression chamber oil
supply hole communicates with the first compression chamber after a
time point when a suction in the first compression chamber is
completed, and the outlet of the second compression chamber oil
supply hole may be formed at a position where the second
compression chamber oil supply hole communicates with the second
compression chamber after a time point when a suction in the second
compression chamber is competed. This may result in suppressing an
increase in a specific volume of refrigerant sucked by pressure of
oil to be supplied, thereby reducing suction loss of the
compressor.
[0028] When a crank angle of a position where an outer
circumferential surface of a suction end of the orbiting wrap is in
contact with an inner circumferential surface of the fixed wrap is
0.degree., the outlet of the first compression chamber oil supply
hole may be formed in a range where pockets forming the first
compression chamber respectively at crank angles of 0.degree.,
90.degree., and 180.degree. overlap, and the outlet of the second
compression chamber oil supply hole may be formed in a range where
pockets forming the second compression chamber respectively at
crank angles of 180.degree., 260.degree., and 320.degree. overlap.
Accordingly, the first compression chamber oil supply hole and the
second compression chamber oil supply hole can communicate with the
compression chambers, respectively, at arbitrary crank angles.
[0029] An outlet of the second compression chamber oil supply hole
may be blocked with respect to the second compression chamber in
the first oil supply section, and an outlet of the first
compression chamber oil supply hole may be blocked with respect to
the first compression chamber in the second oil supply section.
This may prevent the first compression chamber and the second
compression chamber from communicating with each other through the
compression chamber oil supply holes.
[0030] The outlet of the first compression chamber oil supply hole
may be formed in a range of 0.degree. to 90.degree. and the outlet
of the second compression chamber oil supply hole may be formed in
a range of 180.degree. to 260.degree. in a first pressure ratio
section. The outlet of the first compression chamber oil supply
hole may be formed in a range of 90.degree. to 180.degree. and the
outlet of the second compression chamber oil supply hole may be
formed in a range of 260.degree. to 320.degree. in a second
pressure ratio section greater than the first pressure ratio
section. The outlet of the first compression chamber oil supply
hole may be formed in a range of 180.degree. to 250.degree. and the
outlet of the second compression chamber oil supply hole may be
formed in a range of 320.degree. to 380.degree. in a third pressure
ratio section greater than the second pressure ratio section.
Accordingly, within an arbitrary pressure ratio range, the first
compression chamber oil supply hole and the second compression
chamber oil supply hole can be formed at positions where the oil
supply holes communicate with the compression chambers,
respectively, so as to prevent leakage between the compression
chambers and minimize interruption of oil supply to each
compression chamber.
[0031] Here, the first compression chamber oil supply hole and the
second compression chamber oil supply hole may be formed through
the orbiting end plate.
[0032] In this case, the orbiting scroll may be provided with an
oil accommodating portion communicating with the inner space of the
casing, and the first compression chamber oil supply hole and the
second compression chamber oil supply hole may communicate with the
oil accommodating portion.
[0033] The orbiting scroll may be provided with a rotating shaft
coupling portion formed therethrough in an axial direction such
that a rotating shaft is inserted. An eccentric portion bearing may
be fitted onto an inner circumferential surface of the rotating
shaft coupling portion. The eccentric portion bearing may be formed
to be shorter than the rotating shaft coupling portion in length,
such that the oil accommodating portion can be formed in an annular
shape between an end of the eccentric portion bearing and the inner
circumferential surface of the rotating shaft coupling portion.
[0034] A first pressure reducing member may be provided in the
first compression chamber oil supply hole, and a second pressure
reducing member may be provided in the second compression chamber
oil supply hole. An outer diameter of the first pressure reducing
member may be smaller than an inner diameter of the first
compression chamber oil supply hole, and an outer diameter of the
second pressure reducing member may be smaller than an inner
diameter of the second compression chamber oil supply hole.
BRIEF DESCRIPTION OF THE DRAWINGS
[0035] FIG. 1 is a diagram illustrating a refrigeration cycle
apparatus to which a bottom-compression type scroll compressor in
accordance with one implementation of the present disclosure is
applied.
[0036] FIG. 2 is a longitudinal sectional view of a
bottom-compression type scroll compressor in accordance with an
implementation.
[0037] FIG. 3 is an enlarged longitudinal sectional view of a
compression unit in FIG. 2.
[0038] FIG. 4 is a sectional view taken along the line "IV-IV" of
FIG. 3.
[0039] FIG. 5 is an assembled perspective view of a compression
unit in accordance with an implementation.
[0040] FIG. 6 is an exploded perspective view of the compression
unit according to FIG. 5, viewed from the top.
[0041] FIG. 7 is an exploded perspective view of the compression
unit according to FIG. 5, viewed from the bottom.
[0042] FIG. 8 is a perspective view of an orbiting scroll in
accordance with an implementation of the present disclosure.
[0043] FIG. 9 is a planar view of the orbiting scroll according to
FIG. 8, viewed from the top.
[0044] FIG. 10 is a sectional view taken along the line "V-V" in
FIG. 9, which illustrates a first compression chamber oil supply
hole of the orbiting scroll.
[0045] FIG. 11 is a sectional view taken along the line "VI-VI" in
FIG. 9, which illustrates a second compression chamber oil supply
hole of the orbiting scroll.
[0046] FIG. 12 is a planar view illustrating an appropriate
position of an outlet of the first compression chamber oil supply
hole in FIG. 8.
[0047] FIG. 13 is a planar view illustrating an appropriate
position of an outlet of the second compression chamber oil supply
hole in FIG. 8.
[0048] FIG. 14 is a planar view, when viewing the orbiting scroll
from the bottom, for explaining appropriate spaced distances of the
first compression chamber oil supply hole and the second
compression chamber oil supply hole in FIG. 8 from an orbiting
wrap.
[0049] FIG. 15 is a schematic view illustrating open sections of
the respective compression chamber oil supply holes according to
positions of the first compression chamber oil supply hole and the
second compression chamber oil supply hole in accordance with an
implementation of the present disclosure.
[0050] FIG. 16 is a longitudinal sectional view illustrating
another implementation of a scroll compressor, to which the
compression chamber oil supply holes according to the present
disclosure are applied.
DETAILED DESCRIPTION
[0051] Description will now be given in detail of a scroll
compressor according to exemplary embodiments disclosed herein,
with reference to the accompanying drawings. Hereinafter, a
description will be given by defining an axial direction and a
radial direction based on a rotating shaft. That is, for the sake
of explanation, a lengthwise direction of a rotating shaft is
defined as the axial direction (or gravity direction) of the
compressor, and a transverse direction of the rotating shaft is
defined as a radius of the compressor.
[0052] In addition, a description will be given of a high-pressure
type scroll compressor, which is a vertical type scroll compressor
with a motor unit and a compression unit arranged in a vertical
direction and is also a bottom-compression type scroll compressor
with the compression unit located below the motor unit, and in
which a refrigerant suction pipe is directly connected to the
compression unit and a refrigerant discharge pipe communicates with
an inner space of a casing.
[0053] FIG. 1 is a diagram illustrating a refrigeration cycle
apparatus to which a bottom-compression type scroll compressor in
accordance with one implementation of the present disclosure is
applied.
[0054] Referring to FIG. 1, a refrigeration cycle apparatus to
which the scroll compressor according to the implementation is
applied may be configured such that a compressor 10, a condenser
20, an expansion apparatus 30, and an evaporator 40 define a closed
loop. The condenser 20, the expansion apparatus 30, and the
evaporator 40 may be sequentially connected to a discharge side of
the compressor 10 and a discharge side of the evaporator 40 may be
connected to a suction side of the compressor 10.
[0055] Accordingly, refrigerant compressed in the compressor 10 may
be discharged toward the condenser 20, and then sucked back into
the compressor 10 sequentially through the expansion apparatus 30
and the evaporator 40. The series of processes may be repeatedly
carried out.
[0056] FIG. 2 is a longitudinal view illustrating a
bottom-compression type scroll compressor in accordance with an
implementation of the present disclosure, FIG. 3 is an enlarged
longitudinal view illustrating a compression unit in FIG. 2, and
FIG. 4 is a sectional view taken along the line "IV-IV" of FIG.
3.
[0057] Referring to these drawings, the scroll compressor according
to the implementation of the present disclosure is of a
high-pressure type and a bottom-compression type. Hereinafter, it
will be abbreviated as a scroll compressor and described.
[0058] A scroll compressor according to an implementation may
include a driving motor 120 disposed in an upper portion of a
casing 110, and a main frame 130, an orbiting scroll 150, a fixed
scroll 140, and a discharge cover 160 sequentially disposed below
the driving motor 120. In general, the driving motor 120 may
constitute a motor unit, and the main frame 130, the orbiting
scroll 150, the fixed scroll 140, and the discharge cover 160 may
constitute a compression unit.
[0059] The motor unit may be coupled to an upper end of a rotating
shaft 125 to be explained later, and the compression unit may be
coupled to a lower end of the rotating shaft 125. Accordingly, the
compressor 10 may have the bottom-compression type structure
described above, and the compression unit may be connected to the
motor unit by the rotating shaft 125 to be operated by a rotational
force of the motor unit.
[0060] Referring to FIG. 2, the casing 110 according to the
implementation may include a cylindrical shell 111, an upper shell
112, and a lower shell 113. The cylindrical shell 112 may be formed
in a cylindrical shape with upper and lower ends open. The upper
shell 112 may be coupled to cover the opened upper end of the
cylindrical shell 111. The lower shell 113 may be coupled to cover
the opened lower end of the cylindrical shell 111.
[0061] Accordingly, the inner space 110a of the casing 110 may be
sealed. The sealed inner space 110a of the casing 110 may be
divided into a lower space S1 and an upper space S2 based on the
driving motor 120. An oil storage space S3 may be separately
defined below the lower space S1 based on the compression unit. The
lower space S1 may define a discharge space, and the upper space S2
may define an oil separation space.
[0062] The driving motor 120 and the main frame 130 may be fixedly
inserted into the cylindrical shell 111. An outer circumferential
surface of the driving motor 120 and an outer circumferential
surface of the main frame 130 may be spaced apart from an inner
circumferential surface of the cylindrical shell 111 by a preset
interval, thereby defining an oil recovery passage (no reference
numeral given). This will be described again later together with
the oil recovery passage.
[0063] A refrigerant suction pipe 115 may be coupled through a side
surface of the cylindrical shell 111. The refrigerant suction pipe
115 may be coupled through the cylindrical shell 111 forming the
casing 110 in a radial direction.
[0064] The refrigerant suction pipe 115 may be formed in an L-like
shape. One end of the refrigerant suction pipe 115 may be coupled
through the cylindrical shell 111 so as to communicate directly
with a first suction passage 1912 of the discharge cover 160 to be
explained later, which defines a compression unit. In other words,
the refrigerant suction pipe 115 may be connected to a suction
passage 190 to be described later at a position lower than a
compression chamber V in an axial direction. Accordingly, in this
implementation, as the suction passage 190 is formed in the oil
storage space S3 which is an empty space below the compression
unit, a suction passage opening and closing valve 195 to be
described later may be disposed to operate in the axial direction
in a bottom-compression manner, without extending a length of the
compressor.
[0065] Another end of the refrigerant suction pipe 115 may be
connected to an accumulator 50 outside the cylindrical shell 111.
The accumulator 50 may be connected to an outlet side of the
evaporator 40 through a refrigerant pipe. Accordingly, while
refrigerant flows from the evaporator 40 to the accumulator 50,
liquid refrigerant may be separated in the accumulator 50, and only
gaseous refrigerant may be directly introduced into the compression
chamber V through the refrigerant suction pipe 115.
[0066] A terminal bracket (not shown) may be coupled to an upper
portion of the cylindrical shell 111 or the upper shell 112, and a
terminal (not shown) for transmitting external power to the driving
motor 120 may be coupled through the terminal bracket.
[0067] A refrigerant discharge pipe 116 may be coupled through an
upper portion of the upper shell 112 to communicate with the inner
space 110a of the casing 110. The refrigerant discharge pipe 116
may correspond to a passage through which compressed refrigerant
discharged from the compression unit to the inner space 110a of the
casing 110 is externally discharged toward the condenser 20.
[0068] The refrigerant discharge pipe 116 may be provided therein
with an oil separator (not shown) for separating oil from
refrigerant discharged from the compressor 10 to the condenser 20,
or a check valve (not shown) for suppressing refrigerant discharged
from the compressor 10 from flowing back into the compressor
10.
[0069] Hereinafter, a driving motor constituting the motor unit
will be described.
[0070] Referring to FIG. 2, the driving motor 120 according to the
implementation may include a stator 121 and a rotor 122. The stator
121 may be fixed onto the inner circumferential surface of the
cylindrical shell 111, and the rotor 122 may be rotatably disposed
in the stator 121.
[0071] The stator 121 may include a stator core 1211 and a stator
coil 1212.
[0072] The stator core 1211 may be formed in a cylindrical shape
and may be shrink-fitted onto the inner circumferential surface of
the cylindrical shell 111. A plurality of recessed surfaces may be
formed in a D-cut shape recessed into an outer circumferential
surface of the stator core 1211 along the axial direction, and
disposed at preset intervals along a circumferential direction.
[0073] The recessed surfaces 1211a may be spaced apart from the
inner circumferential surface of the cylindrical shell 111 to
define a first oil recovery passage (not shown) through which oil
passes. Accordingly, oil separated from refrigerant in the upper
space S2 may move to the lower space S1 through the first oil
recovery passage, and then return into the oil storage space S3
through a second oil recovery passage (no reference numeral
given).
[0074] The stator coil 1212 may be wound around the stator core
1211 and may be electrically connected to an external power source
through a terminal (not shown) that is coupled through the casing
110. An insulator 1213, which is an insulating member, may be
inserted between the stator core 1211 and the stator coil 1212.
[0075] The insulator 1213 may extend long to both sides in the
axial direction to accommodate a bundle of the stator coil 1212 in
the radial direction, and a portion of the insulator 1213 which
extends downwardly may configure an oil separation portion (no
reference numeral given) to prevent refrigerant discharged into the
lower space S1 from being mixed with oil recovered from the upper
space S2.
[0076] The rotor 122 may include a rotor core 1221 and permanent
magnets 1222.
[0077] The rotor core 1221 may be formed in a cylindrical shape,
and may be rotatably inserted into the stator core 1211 with a
preset gap therebetween. The permanent magnets 1222 may be embedded
in the rotor core 1221 at preset intervals along a circumferential
direction.
[0078] In addition, a balance weight 123 may be coupled to a lower
end of the rotor core 1221. Alternatively, the balance weight 123
may be coupled to a shaft portion 1251 of a rotating shaft 125 to
be described later.
[0079] The rotating shaft 125 may be coupled to the center of the
rotor 122. An upper end portion of the rotating shaft 125 may be
press-fitted into the rotor 122, and a lower end portion may be
rotatably inserted into the main frame 130 to be supported in the
radial direction.
[0080] The main frame 130 may be provided with a main bearing 171
configured as a bush bearing to support the lower end portion of
the rotating shaft 125. Accordingly, the rotating shaft 125 may
transfer the rotational force of the motor unit 120 to the orbiting
scroll 150 of the compression unit. Accordingly, the orbiting
scroll 150 eccentrically coupled to the rotating shaft 125 may
perform an orbiting motion with respect to the fixed scroll
140.
[0081] Referring to FIG. 2, the rotating shaft 125 may include a
shaft portion 1251, a first bearing portion 1252, a second bearing
portion 1253, and an eccentric portion 1254.
[0082] The shaft portion 1251 may be a portion constituting the
upper half of the rotating shaft 125. The shaft portion 1251 may be
formed in a solid cylindrical shape, and the rotor 122 may be
press-fitted into an upper portion of the shaft portion 1251.
[0083] The first bearing portion 1252 may be a portion extending
from a lower end of the shaft portion 1251. The first bearing
portion 1252 may be inserted into a main bearing hole 133a of the
main frame 130 to be described later so as to be supported in the
radial direction.
[0084] The second bearing portion 1253 may be a portion
corresponding to a lower end of the shaft portion 1251. The second
bearing portion 1253 may be inserted into a sub bearing hole 143a
of the fixed scroll 140 to be described later so as to be supported
in the radial direction. The second bearing portion 1253 may be
coaxially disposed with respect to the first bearing portion 1252
so as to have the same axial center.
[0085] The eccentric portion 1254 may be formed between a lower end
of the first bearing portion 1252 and an upper end of the second
bearing portion 1253. The eccentric portion 1254 may be inserted
into a rotating shaft coupling portion 333 of the orbiting scroll
150 to be described later.
[0086] The eccentric portion 1254 may be eccentric with respect to
the first bearing portion 1252 or the second bearing portion 1253
in the radial direction. Accordingly, when the rotating shaft 125
rotates, the orbiting scroll 150 may perform an orbiting motion
with respect to the fixed scroll 140.
[0087] Meanwhile, the rotating shaft 125 may include an oil supply
passage 126 formed therein to supply oil to the first bearing
portion 1252, the second bearing portion 1252, and the eccentric
portion 1254. The oil supply passage 126 may include an inner oil
passage 1261 formed in the rotating shaft along the axial
direction.
[0088] As the compression unit is located below the motor unit 120,
the inner oil passage 1261 may be formed in a grooving manner from
the lower end of the rotating shaft 125 approximately to a lower
end or a middle height of the stator 121 or up to a position higher
than an upper end of the first bearing portion 1252. Of course,
according to circumstances, the inner oil passage 1261 may also be
formed through the rotating shaft 125 in the axial direction.
[0089] In addition, an oil feeder 127 for pumping up oil filled in
the oil storage space S3 may be coupled to the lower end of the
rotating shaft 125, namely, a lower end of the second bearing
portion 1253. The oil feeder 127 may include an oil suction pipe
1271 inserted into the inner oil passage 1261 of the rotating shaft
125, and a blocking member 1272 accommodating the oil supply pipe
1271 to block an introduction of foreign materials. The oil suction
pipe 1271 may extend downward through the discharge cover 160 to be
immersed in the oil filled in the oil storage space S3.
[0090] The rotating shaft 125 may be provided with a plurality of
oil holes communicating with the inner oil passage 1261 to guide
oil moving upward along the inner oil passage 1261 toward the first
and second bearing portions 1252 and 1253 and the eccentric portion
1254.
[0091] The plurality of oil holes may penetrate from an inner
circumferential surface of the inner oil passage 1261 to outer
circumferential surfaces of the bearing portions 1252 and 1253 and
the eccentric portion 1254. The plurality of oil holes may
constitute the oil supply passage 126 together with the inner oil
passage 1261, and include a first oil hole 1262a, a second oil hole
1262b, and a third oil hole 1262c.
[0092] The first oil hole 1262a may be formed from the inner
circumferential surface of the inner oil passage 1261 to the outer
circumferential surface of the first bearing portion 1252 in a
penetrating manner, and the second oil hole 1262b may be formed
from the inner circumferential surface of the inner oil passage
1261 to the outer circumferential surface of the second bearing
portion 1253 in a penetrating manner, and the third oil hole 1262c
may be formed from the inner circumferential surface of the inner
oil passage 1261 to the outer circumferential surface of the
eccentric portion 1254 in a penetrating manner. In other words, the
second oil hole 1262b, the third oil hole 1262c, and the first oil
hole 1262a may be sequentially formed from the lower end to the
upper end of the rotating shaft 125.
[0093] In addition, a first oil groove 1263a may be formed on the
outer circumferential surface of the first bearing portion 1252.
The first oil groove 1263a may communicate with the inner oil
passage 1261 through the first oil hole 1262a. A second oil groove
1263b may be formed on the second bearing portion 1253 of the
rotating shaft 125. The second oil groove 1263b may communicate
with the inner oil passage 1261 through the second oil hole
1262b.
[0094] In addition, a third oil groove 1263c may be formed on the
outer circumferential surface of the eccentric portion 1254. The
third oil groove 1263c may communicate with the inner oil passage
1261 through the third oil hole 1262c. Accordingly, oil which moves
from the inner oil passage 1261 to each of the oil grooves 1263a,
1263b, and 1263c through each of the oil holes 1262a, 1262b, and
1262c may be evenly spread on the outer circumferential surface of
each of the bearing portions 1252 and 1253 and the outer
circumferential surface of the eccentric portion 1254, thereby
lubricating each bearing surface.
[0095] Here, the oil moving to the first oil groove 1263a of the
first bearing portion 1252 or the oil moving to the third oil
groove 1263c of the eccentric portion 1254 may flow to an oil
accommodating portion 155 to be described later. And, this oil may
be supplied to the compression chamber through a compression
chamber oil supply hole 156 provided in the orbiting scroll 150 to
be described later. The compression chamber oil supply hole will be
described again later together with the orbiting scroll.
[0096] Hereinafter, the compression unit will be described. FIG. 5
is a perspective view of a compression unit in an assembled state
in accordance with an implementation, FIG. 6 is an exploded
perspective view of the compression unit according to FIG. 5,
viewed from the top, and FIG. 7 is an exploded perspective view of
the compression unit according to FIG. 5, viewed from the
bottom.
[0097] Referring to FIGS. 5 to 7, the main frame 130 according to
the implementation may include a frame end plate 131, a frame side
wall portion 132, a main bearing portion 133, a scroll
accommodating portion 134, and a scroll support portion 135.
[0098] The frame end plate 131 may be formed in an annular shape
and installed below the driving motor 120. Accordingly, the lower
space S1 of the casing 110 may be separated from the oil storage
space S3 by the frame end plate 131.
[0099] The frame side wall portion 132 may extend in a cylindrical
shape from an edge of a lower surface of the frame end plate 131,
and an outer circumferential surface of the frame side wall portion
132 may be fixed to the inner circumferential surface of the
cylindrical shell 111 in a shrink-fitting or welding manner.
[0100] A scroll accommodating portion 134 to be explained later may
formed inside the frame side wall portion 132. The orbiting scroll
150 to be described later may be accommodated in the scroll
accommodating portion 134 so as to perform an orbiting motion. To
this end, an inner diameter of the frame side wall portion 132 may
be greater than an outer diameter of an orbiting end plate 151 to
be described later.
[0101] A plurality of frame discharge holes 132a may be formed at
the frame side wall portion 132. The plurality of frame discharge
holes 132a may be formed through the frame side wall portion 132 in
the axial direction and disposed at preset intervals along a
circumferential direction.
[0102] The frame discharge holes (hereinafter, referred to as
second discharge holes) 132a may be formed to correspond to scroll
discharge holes 142a of the fixed scroll 140 to be described later,
and define a first refrigerant discharge passage (no reference
numeral given) together with the scroll discharge holes 142a.
[0103] Also, a plurality of frame oil recovery grooves
(hereinafter, referred to as first oil recovery grooves) 132b may
be formed on an outer circumferential surface of the frame side
wall portion 132 with the second discharge holes 132a interposed
therebetween. The plurality of first oil recovery grooves 132b may
be formed in the axial direction at preset intervals along the
circumferential direction.
[0104] The first oil recovery grooves 132b may be formed to
correspond to scroll oil recovery groove 142b of the fixed scroll
140, which will be described later, and define a second oil
recovery passage together with the scroll oil recovery grooves 142b
of the fixed scroll 140.
[0105] The main bearing portion 133 may protrude upward from an
upper surface of a central portion of the frame end plate 131
toward the driving motor 120. The main bearing portion 133 may be
provided with a main bearing hole 133a formed therethrough in a
cylindrical shape along the axial direction. A main bearing 171
configured as a bush bearing may be firmly fitted onto an inner
circumferential surface of the main bearing hole 133a. The main
bearing portion 133 of the rotating shaft 125 may be fitted onto
the main bearing 171 to be supported in the radial direction.
[0106] The scroll accommodating portion 134 may be a space defined
by a lower surface of the frame end plate 131 and the inner
circumferential surface of the frame side wall portion 132. An
orbiting end plate 151 of the orbiting scroll 150 to be described
later may be supported in the axial direction by the lower surface
of the frame end plate 131, and accommodated in the frame side wall
portion 132 in a manner that its outer circumferential surface is
spaced apart from the inner circumferential surface of the frame
side wall portion 132 by a preset interval (for example, an
orbiting radius). Accordingly, the inner diameter of the frame side
wall portion 132 constituting the scroll accommodating portion 134
may be greater than the outer diameter of the orbiting end plate
151 by the orbiting radius or more.
[0107] In addition, the frame side wall portion 132 defining the
scroll accommodating portion 134 may have a height (depth) that is
greater than or equal to a thickness of the orbiting end plate 151.
Accordingly, while the frame side wall portion 132 is supported on
the upper surface of the fixed scroll 140, the orbiting scroll 150
may perform an orbiting motion in the scroll accommodating portion
134.
[0108] The scroll support portion 135 may be formed in an annular
shape on the lower surface of the frame end plate 131 that faces
the orbiting end plate 151 of the orbiting scroll 150 to be
described later. Accordingly, an Oldham ring 180 may be pivotably
inserted between an outer circumferential surface of the scroll
support portion 135 and the inner circumferential surface of the
frame side wall portion 132.
[0109] In addition, the scroll support portion 135 may have a lower
surface formed flat, so that a back pressure sealing member 1515
provided on the orbiting end plate 151 of the orbiting scroll 150
to be described later is in contact with the lower surface in a
sliding manner.
[0110] The back pressure sealing member 1515 may be formed in an
annular shape, thereby defining an oil accommodating portion 155
between the scroll support portion 135 and the orbiting end plate
151. Accordingly, oil flowing into the oil accommodating portion
155 through the third oil hole 1262c of the rotating shaft 125 may
be introduced into the compression chamber V through a compression
chamber oil supply hole 156 of the orbiting scroll 150 to be
described later.
[0111] Hereinafter, the fixed scroll will be described.
[0112] Referring to FIGS. 5 to 7 again, the fixed scroll 140
according to the implementation may include a fixed end plate 141,
a fixed side wall portion 142, a sub bearing portion 143, and a
fixed wrap 144.
[0113] The fixed end plate 141 may be formed approximately in a
disk shape, and a sub bearing hole 143a forming the sub bearing
portion 143 to be described later may be formed through a center of
the fixed end plate 141 in the axial direction. Discharge ports
141a and 141b may be formed around the sub bearing hole 143a. The
discharge ports 141a and 141b may communicate with a discharge
chamber Vd so that compressed refrigerant is moved into a discharge
space S4 of the discharge cover 160 to be explained later.
[0114] Only one discharge port may be provided to communicate with
both of a first compression chamber V1 and a second compression
chamber V2 to be described later. In the illustrated
implementation, however, the first discharge port 141a may
communicate with the first compression chamber V1 and the second
discharge port 141b may communicate with the second compression
chamber V2. Accordingly, refrigerant compressed in the first
compression chamber V1 and refrigerant compressed in the second
compression chamber V2 may be independently discharged through the
different discharge ports.
[0115] The fixed side wall portion 142 may extend in an annular
shape from an edge of an upper surface of the fixed end plate 141
in the axial direction. The fixed side wall portion 142 may be
coupled to face the frame side wall portion 132 of the main frame
31 in the axial direction.
[0116] A plurality of scroll discharge holes (hereinafter, referred
to as first discharge holes) 142a may be formed through the fixed
side wall portion 142 in the axial direction and communicate with
the frame discharge holes 132a to define the first refrigerant
discharge passage together with the frame discharge holes 132a.
[0117] Scroll oil recovery grooves (hereinafter, referred to as
second oil recovery grooves) 142b may be formed on the outer
circumferential surface of the fixed side wall portion 142. The
second oil recovery grooves 142b may communicate with the first oil
recovery grooves 132b provided at the main frame 130 to guide oil
recovered along the first oil recovery grooves 132b to the oil
storage space S3. Accordingly, the first oil recovery grooves 132b
and the second oil recovery grooves 142b may define the second oil
recovery passage together with oil recovery grooves 1612b and 162b
of a flange portion 162 to be described later.
[0118] Meanwhile, a second suction passage 1921 may be formed in
the fixed side wall portion 142 to communicate with a first suction
passage 1912 formed in the discharge cover 160 to be described
later. The second suction passage 1921 may define a suction
port.
[0119] The second suction passage 1921 may be formed within a range
of a suction chamber Vs of the compression unit to communicate with
the suction chamber Vs. A suction passage opening and closing valve
195 may be installed in the second suction passage 1921 to
selectively open or close a suction passage 190 which includes the
second suction passage 1921 and the first suction passage 1912. The
suction passage opening and closing valve 195 may also be referred
to as a non-return valve, a suction valve, or a check valve.
[0120] The suction passage opening and closing valve 195 may be
provided at a boundary surface between the first suction passage
1912 and the second suction passage 1921 to allow a fluid movement
from the first suction passage 1912 to the second suction passage
1921 while blocking a reverse fluid movement from the second
suction passage 1921 to the first suction passage 1912.
[0121] Accordingly, during the operation of the compressor,
refrigerant sucked through the refrigerant suction pipe 115 may be
introduced into the suction chamber Vs through the suction passage
190 including the first suction passage 1912 and the second suction
passage 1921. On the other hand, when the compressor is stopped,
the suction passage opening and closing valve 195 may close the
suction passage 190 so that high-temperature oil contained in the
oil storage space of the casing can be prevented from flowing back
into the refrigerant suction pipe 115 together with
high-temperature refrigerant compressed in the compression chamber.
The suction passage including the second suction passage will be
described later.
[0122] The sub bearing portion 143 may extend in the axial
direction from a central portion of the fixed end plate 141 toward
the discharge cover 160. The sub bearing portion 143 may be
provided with a sub bearing hole 143a formed in a cylindrical shape
through a center thereof along the axial direction. A sub bearing
172 configured as a bush bearing may be fitted onto an inner
circumferential surface of the sub bearing hole 143a.
[0123] Therefore, the lower end of the rotating shaft 125 may be
inserted into the sub bearing portion 143 of the fixed scroll 140
to be supported in the radial direction, and the eccentric portion
1254 of the rotating shaft 125 may be supported by the upper
surface of the fixed end plate 141 defining the surrounding of the
sub bearing portion 143.
[0124] A fixed wrap 144 may extend from the upper surface of the
fixed end plate 141 toward the orbiting scroll 150 in the axial
direction. The fixed wrap 144 may be engaged with an orbiting wrap
152 to be described later to define the compression chamber V. The
fixed wrap 144 will be described later together with the orbiting
wrap 152.
[0125] Hereinafter, the orbiting scroll will be described.
[0126] Referring to FIGS. 5 to 7, the orbiting scroll 150 according
to the implementation may include an orbiting end plate 151, an
orbiting wrap 152, and a rotating shaft coupling portion 153.
[0127] The orbiting end plate 151 may be formed approximately in a
disk shape. A back pressure sealing groove 151a into which the back
pressure sealing member 1515 is inserted may be formed in an upper
surface of the orbiting end plate 151. The back pressure sealing
groove 151a may be formed at a position facing the scroll support
portion 135 of the main frame 130.
[0128] The back pressure sealing groove 151a may be formed in an
annular shape to surround a rotating shaft coupling portion 153 to
be described later, and may be eccentric with respect to an axial
center of the rotating shaft coupling portion 153. Accordingly,
even if the orbiting scroll 150 performs an orbiting motion, a back
pressure chamber (no reference numeral given) having a constant
range may be defined between the orbiting scroll 150 and the scroll
support portion 135 of the main frame 130.
[0129] The orbiting end plate 151 may be further provided with a
compression chamber oil supply hole 156. One end of the compression
chamber oil supply hole 156 may communicate with the oil
accommodating portion 155, and another end may communicate with an
intermediate pressure chamber of the compression chamber.
Accordingly, oil stored in the oil accommodating portion 155 may be
supplied to the compression chamber V through the compression
chamber oil supply hole 156 to lubricate the compression
chamber.
[0130] The orbiting wrap 152 may extend from a lower surface of the
orbiting end plate 151 toward the fixed scroll 140. The orbiting
wrap 152 may be engaged with the fixed wrap 144 to define the
compression chamber V.
[0131] The orbiting wrap 152 may be formed in an involute shape
together with the fixed wrap 144. However, the orbiting wrap 152
and the fixed wrap 144 may be formed in various shapes other than
the involute shape. For example, as illustrated in FIG. 4, the
orbiting wrap 152 may be formed in a substantially elliptical shape
in which a plurality of arcs having different diameters and origins
are connected and the outermost curve may have a major axis and a
minor axis. The fixed wrap 144 may also be formed in a similar
manner.
[0132] An inner end portion of the orbiting wrap 152 may be formed
at a central portion of the orbiting end plate 151, and the
rotating shaft coupling portion 153 may be formed through the
central portion of the orbiting end plate 151 in the axial
direction.
[0133] The eccentric portion 1254 of the rotating shaft 125 may be
rotatably inserted into the rotating shaft coupling portion 153. An
outer circumferential part of the rotating shaft coupling portion
153 may be connected to the orbiting wrap 152 to form the
compression chamber V together with the fixed wrap 144 during a
compression process.
[0134] The rotating shaft coupling portion 153 may be formed at a
height at which it overlaps the orbiting wrap 152 on the same
plane. That is, the rotating shaft coupling portion 153 may be
disposed at a height at which the eccentric portion 1254 of the
rotating shaft 125 overlaps the orbiting wrap 152 on the same
plane. Accordingly, repulsive force and compressive force of
refrigerant may cancel each other while being applied to the same
plane based on the orbiting end plate 151, and thus inclination of
the orbiting scroll 150 due to interaction between the compressive
force and the repulsive force may be suppressed.
[0135] In addition, the rotating shaft coupling portion 153 may be
provided with a concave portion 153a that is formed on an outer
circumferential surface thereof, namely, an outer circumferential
surface facing an inner end portion of the fixed wrap 144, to be
engaged with a protruding portion 144a of the fixed wrap 144 to be
described later. A convex portion 153b may be formed at one side of
the concave portion 153a. The convex portion 153b may be formed at
an upstream side along a direction in which the compression chamber
V is formed, and have a thickness increasing from an inner
circumferential surface to an outer circumferential surface of the
rotating shaft coupling portion 153.
[0136] This may extend a compression path of the first compression
chamber V1 immediately before discharge, and consequently the
compression ratio of the first compression chamber V1 can be
increased close to a pressure ratio of the second compression
chamber V2. The first compression chamber V1 is a compression
chamber formed between an inner surface of the fixed wrap 144 and
an outer surface of the orbiting wrap 152, and will be described
later separately from the second compression chamber V2.
[0137] An arcuate compression surface 153c having an arcuate shape
may be provided at another side of the concave portion 153a. The
diameter of the arcuate compression surface 153c may be determined
by a thickness of the inner end portion of the fixed wrap 144
(i.e., a thickness of a discharge end) and an orbiting radius of
the orbiting wrap 152.
[0138] For example, when the thickness of the inner end portion of
the fixed wrap 144 increases, the diameter of the arcuate
compression surface 153c may increase. As a result, a wrap
thickness of the orbiting wrap around the arcuate compression
surface 153c may increase to ensure durability and thus the
compression path may extend to increase the compression ratio of
the second compression chamber V2 to that extent.
[0139] The protruding portion 144a protruding toward the outer
circumferential surface of the rotating shaft coupling portion 153
may be formed near the inner end portion (suction end or start end)
of the fixed wrap 144 corresponding to the rotating shaft coupling
portion 153. Accordingly, a contact portion 144b may protrude from
the protruding portion 144a to be engaged with the concave portion
153a.
[0140] In other words, the inner end portion of the fixed wrap 144
may be formed to have a larger thickness than other portions. As a
result, wrap strength at the inner end portion of the fixed wrap
144, which is subjected to the strongest compressive force on the
fixed wrap 144, may increase so as to enhance durability.
[0141] On the other hand, referring to FIG. 4, the compression
chamber V may be formed in a space defined by the fixed end plate
141, the fixed wrap 144, the orbiting end plate 151, and the
orbiting wrap 152. The compression chamber V may include a first
compression chamber V1 formed between an inner surface of the fixed
wrap 144 and an outer surface of the orbiting wrap 152, and a
second compression chamber V2 formed between an outer surface of
the fixed wrap 144 and an inner surface of the orbiting wrap
152.
[0142] In each of the first compression chamber V1 and the second
compression chamber V2, a suction chamber Vs, an intermediate
pressure chamber Vm, and a discharge chamber Vd may be continuously
formed from outside to inside along an advancing direction of the
wraps.
[0143] Here, the intermediate pressure chamber Vm and the discharge
chamber Vd may be independently formed for each of the first
compression chamber V1 and the second compression chamber V2.
Accordingly, the first discharge port 141a may communicate with a
discharge chamber Vd1 of the first compression chamber V1 and the
second discharge port 141b may communicate with a discharge chamber
Vd2 of the second compression chamber V2.
[0144] On the other hand, the suction chamber Vs may be formed to
be shared by the first compression chamber V1 and the second
compression chamber V2. That is, the suction chamber Vs may be
formed at an outer side than the orbiting wrap 152 based on the
advancing direction of the wrap. Specifically, the suction chamber
Vs may be defined as a space formed in an area that the end of the
orbiting wrap 152 does not reach, namely, outside an orbiting range
of the orbiting wrap 152, in a space formed between the inner
circumferential surface of the fixed side wall portion 142 and an
outer surface of the outermost fixed wrap 144 extending from the
fixed side wall portion 142.
[0145] Accordingly, the second suction passage 1921 may be formed
through the fixed end plate 141 in the axial direction to
communicate with the suction chamber Vs, and the suction passage
opening and closing valve 195 may not interfere with the orbiting
wrap 152 even though it passes through the suction chamber Vs while
moving in the second suction passage 1921 in the axial direction
along the fixed side wall portion 142. This will be described later
again together with the suction passage and the suction passage
opening and closing valve.
[0146] On the other hand, an eccentric portion bearing 173
configured as a bush bearing may be fitted onto the inner
circumferential surface of the rotating shaft coupling portion 153.
The eccentric portion 1254 of the rotating shaft 125 may be
rotatably inserted into the eccentric portion bearing 173.
Accordingly, the eccentric portion 1254 of the rotating shaft 125
may be supported by the eccentric portion bearing 173 in the radial
direction so as to perform a smooth orbiting motion with respect to
the orbiting scroll 150.
[0147] Here, the oil accommodating portion 155 may be formed inside
the rotating shaft coupling portion 153. The oil accommodating
portion 155 may communicate with the compression chamber oil supply
hole 156 that is formed through the orbiting end plate 151 in the
radial direction.
[0148] The oil accommodating portion 155 may formed on the upper
side of the eccentric portion bearing 173. For example, an axial
length of the eccentric portion bearing 173 may be shorter than an
axial length (height) of the rotating shaft coupling portion 153.
Accordingly, a space corresponding to a difference in length
between the eccentric portion bearing 173 and the rotating shaft
coupling portion 153 and the thickness of the eccentric portion
bearing 173 may be formed in an upper end of the eccentric portion
bearing 173. This space may communicate with the third oil hole
1262c or the first oil hole 1262a of the rotating shaft 125 to
define the aforementioned oil accommodating portion 155.
[0149] Alternatively, only one compression chamber oil supply hole
156 may be provided to communicate with any one of the first
compression chamber V1 and the second compression chamber V2.
However, in the illustrated implementation, the compression chamber
oil supply hole 156 may include a first compression chamber oil
supply hole 1561 communicating with the first compression chamber
V1, and a second compression chamber oil supply hole 1562
communicating with the second compression chamber V2.
[0150] For example, one end, namely, an inlet of the first
compression chamber oil supply hole 1561 and one end, namely, an
inlet of the second compression chamber oil supply hole 1562 may
communicate with the oil accommodating portion 155, respectively,
and another end, namely, an outlet of the first compression chamber
oil supply hole 1561 and another end, namely, an outlet of the
second compression chamber oil supply hole 1562 may communicate
with the first compression chamber V1 and the second compression
chamber V2, respectively.
[0151] Specifically, the outlets of the first compression chamber
oil supply hole 1561 and the second compression chamber oil supply
hole 1562 may penetrate through the lower surface of the orbiting
end plate 151 at a time point when suction in each compression
chamber V1 and V2 is completed, namely, at a rotating angle of the
orbiting wrap 152 greater than a rotating angle of the orbiting
wrap 152, at which the suction in each compression chamber V1 and
V2 is completed.
[0152] Accordingly, the outlets of the first compression chamber
oil supply hole 1561 and the second compression chamber oil supply
hole 1562 may be located at a downstream side more than the suction
passage opening and closing valve 195 based on a direction that the
refrigerant is sucked. Accordingly, when the compressor is stopped,
oil which is intended to flow back toward the refrigerant suction
pipe 115 through the first compression chamber oil supply hole 1561
and the second compression chamber oil supply hole 1562 may be
blocked by the suction passage opening and closing valve 195,
thereby preventing oil leakage from the compression chambers V1 and
V2 toward the refrigerant suction pipe 115.
[0153] Hereinafter, the discharge cover will be described.
[0154] Referring back to FIGS. 5 to 7, the discharge cover 160 may
include a cover housing portion 161 and a cover flange portion 162.
The cover housing portion 161 may have a cover space 161a therein
defining the discharge space S4 together with the fixed scroll
140.
[0155] The cover housing portion 161 may include a housing bottom
surface 1611 and a housing side wall surface 1612 extending in the
axial direction from the housing bottom surface 1611 to have a
substantially annular shape.
[0156] Accordingly, the housing bottom surface 1611 and the housing
side wall surface 1612 may define the cover space 161a for
accommodating the outlets of the discharge ports 141a and 141b
provided in the fixed scroll 140 and the inlet of the first
discharge hole 142a, and the cover space 161a may define the
discharge space S4 together with a surface of the fixed scroll 140
inserted into the cover space 161a.
[0157] A cover bearing protrusion 1613 may protrude from a central
portion of the housing bottom surface 1611 toward the fixed scroll
140 in the axial direction, and a through hole 1613a may be formed
through the inside of the cover bearing protrusion 1613 in the
axial direction.
[0158] The sub bearing portion 143 that protrudes from the rear
surface of the fixed scroll 140, namely, the fixed end plate 141 in
a downward direction (axial direction) may be inserted into the
through hole 1613a. A cover sealing member 1614 for sealing a gap
between an inner circumferential surface of the through hole 1613a
and an outer circumferential surface of the sub bearing portion 143
may be inserted into the gap.
[0159] The housing side wall surface 1612 may extend outward from
an outer circumferential surface of the cover housing portion 161
so as to be coupled in close contact with the lower surface of the
fixed scroll 140. In addition, at least one discharge guide groove
1612a may be formed on an inner circumferential surface of the
housing side wall surface 1612 along the circumferential
direction.
[0160] The discharge guide groove 1612a may be recessed outward in
the radial direction, and the first discharge hole 142a of the
fixed scroll 140 defining a first refrigerant discharge passage may
be formed to be positioned inside the discharge guide groove 1612a.
Accordingly, an inner surface of the housing side wall surface 1612
excluding the discharge guide groove 1612a may be brought into
close contact with the outer circumferential surface of the fixed
scroll 140, namely, the outer circumferential surface of the fixed
end plate 141 so as to configure a type of sealing part.
[0161] Here, an entire circumferential angle of the discharge guide
groove 1612a may be formed to be smaller than or equal to an entire
circumferential angle with respect to an inner circumferential
surface of the discharge space S4 except for the discharge guide
groove 1612a. In this manner, the inner circumferential surface of
the discharge space S4 except for the discharge guide groove 1612a
can secure not only a sufficient sealing area but also a
circumferential length for forming the cover flange portion 162 to
be described later.
[0162] The housing side wall surface 1612 may be provided with oil
recovery grooves 1612b formed on an outer circumferential surface
thereof with a preset interval along the circumferential direction
so as to define a third oil recovery groove. For example, the oil
recovery groove 1612b may be formed on the outer circumferential
surface of the housing side wall surface 1612. The oil recovery
groove 1612b may define the third oil recovery groove together with
oil recovery grooves 162b of the cover flange portion 162 to be
described later. The third oil recovery groove of the discharge
cover 160 may define the second oil recovery passage together with
the first oil recovery groove of the main frame 130 and the second
oil recovery groove of the fixed scroll 140.
[0163] The cover flange portion 162 may extend radially from a
portion defining the sealing part, namely, from an outer
circumferential surface of a portion, excluding the discharge guide
groove 1612a, of the housing side wall surface 1612 of the cover
housing portion 161.
[0164] The cover flange portion 162 may be provided with coupling
holes 162a for coupling the discharge cover 160 to the fixed scroll
140 with bolts, and a plurality of oil recovery grooves 162b formed
between the neighboring coupling holes 162a at preset intervals in
the circumferential direction.
[0165] The oil recovery grooves 162b formed on the cover flange
portion 162 may define the third oil recovery groove together with
the oil recovery groove 1612b formed on the housing side wall
surface 1612. The oil recovery grooves 162b formed on the cover
flange portion 162 may be recessed inward (toward a center) in the
radial direction from an outer circumferential surface of the cover
flange portion 162.
[0166] Meanwhile, the first suction passage 1912 may be formed in
the discharge cover 160, and the refrigerant suction pipe 115 may
communicate with the second suction passage 1921 of the fixed
scroll 140 through the first suction passage 1912. The refrigerant
suction pipe 115 inserted through the cylindrical shell 111 may be
inserted into an inlet of the first suction passage 1912 so as to
communicate directly with the first suction passage 1912. An outlet
of the first suction passage 1912 may communicate with the second
suction passage 1921 of the fixed scroll 140. In addition, the
outlet of the first suction passage 1912 may be selectively opened
and closed by the suction passage opening and closing valve 195
inserted into the second suction passage 1921.
[0167] Accordingly, refrigerant circulating in the refrigeration
cycle during the operation of the compressor may flow into the
first suction passage 1912 of the discharge cover 160 through the
refrigerant suction pipe 115. The refrigerant may open the suction
passage opening and closing valve 195 so as to be introduced into
the suction chamber Vs through the second suction passage 1921.
[0168] In the drawings, unexplained reference numeral 21 denotes a
condenser fan, 41 denotes an evaporator fan, and 1911 denotes a
suction guide protrusion.
[0169] Hereinafter, an operation of the high-pressure and
bottom-compression type scroll compressor according to the
implementation will be described.
[0170] That is, when power is applied to the motor unit 120,
rotational force may be generated and the rotor 22 and the rotating
shaft 125 may rotate accordingly. As the rotating shaft 125
rotates, the orbiting scroll 35 eccentrically coupled to the
rotating shaft 125 may perform an orbiting motion by the Oldham
ring 180.
[0171] Accordingly, the volume of the compression chamber V may
gradually decrease from a suction chamber Vs formed at an outer
side of the compression chamber V toward an intermediate pressure
chamber Vm continuously formed toward a center and a discharge
chamber Vd in a central portion.
[0172] Then, refrigerant may move to the accumulator 50
sequentially via the condenser 20, the expansion apparatus 30, and
the evaporator 40 of the refrigeration cycle. The refrigerant may
flow toward the suction chamber Vs forming the compression chamber
V through the refrigerant suction pipe 115.
[0173] The refrigerant sucked into the suction chamber Vs may be
compressed while moving to the discharge chamber Vd via the
intermediate pressure chamber Vm along a movement trajectory of the
compression chamber V. The compressed refrigerant may be discharged
from the discharge chamber Vd to the discharge space S4 of the
discharge cover 60 through the discharge ports 141a and 141b.
[0174] The refrigerant discharged into the discharge space S4 of
the discharge cover 160 may then flow into the inner space 110a of
the casing 110 through the discharge guide groove 1612a of the
discharge cover 160 and the first discharge holes 142a of the fixed
scroll 140. The refrigerant may flow to the lower space S1 between
the main frame 130 and the driving motor 120 and then move toward
the upper space S2 of the casing 110, which is defined above the
driving motor 120, through a gap between the stator 121 and the
rotor 122.
[0175] However, oil may be separated from the refrigerant in the
upper space S2 of the casing 110, and the oil-separated refrigerant
may be discharged to the outside of the casing 110 through the
refrigerant discharge pipe 116 so as to flow to the condenser 20 of
the refrigeration cycle.
[0176] On the other hand, the oil separated from the refrigerant in
the inner space 110a of the casing 110 may be recovered into the
oil storage space S3 defined in the lower portion of the
compression unit through the first oil recovery passage between the
inner circumferential surface of the casing 110 and the stator 121
and the second oil recovery passage between the inner
circumferential surface of the casing 110 and the outer
circumferential surface of the compression unit. This oil may
thusly be supplied to each bearing surface (not shown) through the
oil supply passage 126, and partially supplied into the compression
chamber V. The oil supplied to the bearing surface and the
compression chamber V may be discharged to the discharge cover 160
together with the refrigerant and recovered. This series of
processes may be repeatedly performed.
[0177] On the other hand, when the compressor 10 is stopped, the
refrigeration cycle including the compressor 10 may perform an
operation to enter a so-called pressure equilibrium state. At this
time, the oil or refrigerant filled in the inner space 110a of the
casing 110 may flow back toward the refrigerant suction pipe 115.
Due to the back flow of the oil or refrigerant, a specific volume
of suction refrigerant may be increased and suction loss may be
increased thereby. Also, upon restart of a refrigeration cycle, an
oil shortage may be caused, thereby lowering reliability and
performance of the compressor.
[0178] However, the back flow of the oil or refrigerant may be
suppressed by a suction passage opening and closing valve 195 that
is installed in the middle of the suction passage 190, for example,
in the middle between the first suction passage 1912 and the second
suction passage 1921 so as to configure a kind of check valve. The
suction passage opening and closing valve 195 may block the suction
passage 190 when the compressor is stopped, thereby preventing the
oil or refrigerant in the casing 110 from flowing back toward the
suction passage 190 through the compression unit.
[0179] In this way, in the scroll compressor of the high-pressure
type and the bottom-compression type, as the suction passage
opening and closing valve is installed between an outlet of the
refrigerant suction pipe and an inlet of the compression unit, the
oil or refrigerant in the casing can be quickly prevented from
flowing back to the refrigerant suction pipe through the
compression unit when the compressor is stopped. Accordingly, upon
the restart of the compressor, an increase in a specific volume of
the refrigerant can be suppressed and friction loss due to a
shortage of oil can be reduced, thereby improving compression
efficiency.
[0180] As the suction passage opening and closing valve is operated
in the axial direction, the structure of the suction passage
opening and closing valve can be simplified, which may result in
reducing a fabricating cost and simultaneously improving
responsiveness of the valve, thereby enhancing the compression
efficiency.
[0181] In addition, as the suction passage is formed in the
discharge cover or the fixed scroll, the suction passage may be
formed in an oil storage space located below the compression unit,
so that the compressor can be reduced in size while maintaining its
axial length.
[0182] On the other hand, as described above, when different oil
supply paths (for example, a first oil supply hole and a second oil
supply hole) are formed to communicate individually with the first
and second compression chambers, at least one of the different oil
supply paths may be opened toward the corresponding compression
chamber.
[0183] In particular, oil supply sections (e.g., a first oil supply
section in which the first oil supply hole is open and a second oil
supply section in which the second oil supply hole is open) in
which the different oil supply paths are open to the corresponding
compression chambers may be formed to overlap each other within a
preset crank angle range.
[0184] In other words, oil supply sections (e.g., first and second
oil supply sections) in which the respective oil supply paths are
open may have an overlap section. Then, even if the orbiting scroll
performs the orbiting motion during the operation of the
compressor, at least one oil supply path may be open, such that oil
can be fed to the compression unit without interruption, thereby
suppressing friction loss.
[0185] However, if the first oil supply section and the second oil
supply section overlap each other within a preset crank angle
range, it may be advantageous in terms of oil supply, but may be
disadvantageous in terms of compression efficiency. For example,
when a pressure difference between the first compression chamber
and the second compression chamber occurs, a phenomenon in which
refrigerant compressed in a high-pressure side partially flows back
to a low pressure-side may occur in the section where the first oil
supply section and the second oil supply section overlap each
other. As a result, compression loss may be increased and
compression efficiency may be decreased.
[0186] Therefore, in the implementation of the present disclosure,
a first compression chamber oil supply hole communicating with a
first compression chamber and a second compression chamber oil
supply hole communicating with the second compression chamber may
be individually provided, so as to prevent both the compression
chambers from communicating with each other through the first
compression chamber oil supply hole and the second compression
chamber oil supply hole.
[0187] FIG. 8 is a perspective view of an orbiting scroll in
accordance with an implementation of the present disclosure, FIG. 9
is a planar view of the orbiting scroll according to FIG. 8, viewed
from the top, FIG. 10 is a sectional view taken along the line
"V-V" in FIG. 9, which illustrates a first compression chamber oil
supply hole of the orbiting scroll, and FIG. 11 is a sectional view
taken along the line "VI-VI" in FIG. 9, which illustrates a second
compression chamber oil supply hole of the orbiting scroll.
[0188] Referring to FIGS. 8 and 9, a first compression chamber oil
supply hole 1561 and a second compression chamber oil supply hole
1562 according to an implementation may be formed in the orbiting
end plate 151.
[0189] For example, the first compression chamber oil supply hole
1561 and the second compression chamber oil supply hole 1562 may
penetrate through the inside of the orbiting end plate 151 in the
radial direction from an inner circumferential surface of the
rotating shaft coupling portion 153, and then penetrate through a
side surface of the orbiting end plate 151 facing the fixed end
plate 141. Accordingly, the first compression chamber oil supply
hole 1561 and the second compression chamber oil supply hole 1562
may allow the oil accommodating portion 155, which is provided in
the rotating shaft coupling portion 153, more precisely, the upper
end of the eccentric portion bearing 173, to communicate with the
first compression chamber V1 and the second compression chamber V2,
respectively.
[0190] The first compression chamber oil supply hole 1561 and the
second compression chamber oil supply hole 1562 may have the same
basic configuration, except for positions where outlets of those
oil supply holes communicate with the first compression chamber V1
and the second compression chamber V2, respectively. Hereinafter,
the first compression chamber oil supply hole 1561 and the second
compression chamber oil supply hole 1562 will be described
sequentially.
[0191] Referring to FIGS. 9 and 10, the first compression chamber
oil supply hole 1561 may include a first oil supply inlet portion
1561a, a first oil supply connection portion 1561b, a first oil
supply penetration portion 1561c, and a first oil supply outlet
portion 1561d. Accordingly, oil inside the oil accommodating
portion 155 may be supplied to the first compression chamber V1
sequentially via the first oil supply inlet portion 1561a, the
first oil supply connection portion 1561b, the first oil supply
penetration portion 1561c, and the first oil supply outlet portion
1561d.
[0192] The first oil supply inlet portion 1561a may have an inlet
end communicating with an inner circumferential surface of the oil
accommodating portion 155 to define an inlet of the first
compression chamber oil supply hole 1561. For example, the first
oil supply inlet portion 1561a may be recessed into the upper
surface of the orbiting end plate 151 by a preset depth and extend
in the radial direction. Accordingly, oil contained in the oil
accommodating portion 155 may move to the first oil supply inlet
portion 1561a and spread to the upper surface of the orbiting
scroll 150 at an inner space (e.g., back pressure chamber) of the
back pressure sealing member 1515, thereby smoothly lubricating a
gap between the main frame 130 and the orbiting scroll 150.
[0193] The first oil supply inlet portion 1561a may extend in a
direction in which the back pressure sealing groove 151a is
eccentric from the rotating shaft coupling portion 153 at an inner
side than the back pressure sealing grove 151a. However,
considering the fact that a first pressure reducing member 1565a is
installed inside the first oil supply penetration portion 1561c, a
length of the first oil supply inlet portion 1561a may preferably
be as short as possible.
[0194] The first oil supply connection portion 1561b may extend in
the axial direction from an end of the first oil supply inlet
portion 1561a and be recessed by an intermediate depth of the
orbiting end plate 151. Accordingly, oil flowing into the first oil
supply inlet portion 1561a may move toward the first oil supply
penetration portion 1561c through the first oil supply connection
portion 1561b.
[0195] The first oil supply penetration portion 1561c may be formed
through the inside of the orbiting end plate 151 in the radial
direction. Since the first oil supply penetration portion 1561c may
be made in a direction from an outer circumferential surface to an
inner circumferential surface of the orbiting end plate 151, a
blocking bolt (not shown) may be coupled to an outer end of the
first oil supply penetration portion 1561c, so as to seal the outer
end of the first oil supply penetration portion 1561c.
[0196] The first pressure reducing member 1565a may be inserted
into the oil supply penetration portion 1561c. The first pressure
reducing member 1565a may be configured as a pressure reducing pin
having an outer diameter smaller than an inner diameter of the
first oil supply penetration portion 1561c. Accordingly, oil in the
oil accommodating portion 155 may be decompressed while passing
through the first pressure reducing member 1565a inside the oil
supply penetration portion 1561c and then supplied to the first
compression chamber V1.
[0197] The first oil supply outlet portion 1561d may penetrate
through the lower surface of the orbiting end plate 151 at an end
portion of the first oil supply penetration portion 1561c in the
radial direction. Accordingly, the first compression chamber oil
supply hole 1561 may allow the communication between the oil
accommodating portion 155 and the first compression chamber V1.
[0198] The first oil supply outlet portion 1561d may be formed at a
position spaced apart from an outer circumferential surface of the
outermost orbiting wrap 152 by a preset interval. As described
above, the first oil supply outlet portion 1561d may penetrate
through a surface facing the fixed end plate 141, namely, the lower
surface of the orbiting end plate 151, at the outer end portion of
the first oil supply penetration portion 1561c. The first oil
supply outlet portion 1561d may have an inner diameter which is
smaller than or equal to an inner diameter of the first oil supply
penetration portion 1561c, for example, smaller than a wrap
thickness of the fixed wrap 144.
[0199] On the other hand, the second compression chamber oil supply
hole 1562 may be formed almost similar to the first compression
chamber oil supply hole 1561.
[0200] Referring to FIGS. 9 and 11, the second compression chamber
oil supply hole 1562 may include a second oil supply inlet portion
1562a, a second oil supply connection portion 1562b, a second oil
supply penetration portion 1562c, and a second oil supply outlet
portion 1562d. Accordingly, oil inside the oil accommodating
portion 155 may be supplied to the second compression chamber V2
sequentially via the second oil supply inlet portion 1562a, the
second oil supply connection portion 1562b, the second oil supply
penetration portion 1562c, and the second oil supply outlet portion
1562d.
[0201] The second oil supply inlet portion 1562a may have an inlet
end communicating with an inner circumferential surface of the oil
accommodating portion 155 to define an inlet of the second
compression chamber oil supply hole 1562. For example, the second
oil supply inlet portion 1562a may be recessed into the upper
surface of the orbiting end plate 151 by a preset depth and extend
in the radial direction. Accordingly, oil contained in the oil
accommodating portion 155 may move to the second oil supply inlet
portion 1562a and spread to the upper surface of the orbiting
scroll 150 at an inner space (e.g., back pressure chamber) of the
back pressure sealing member 1515, thereby smoothly lubricating a
gap between the main frame 130 and the orbiting scroll 150.
[0202] The second oil supply inlet portion 1562a may extend in a
direction in which the back pressure sealing groove 151a is
eccentric from the rotating shaft coupling portion 153 at an inner
side than the back pressure sealing grove 151a. However,
considering the fact that a second pressure reducing member 1565a
is installed inside the second oil supply penetration portion
1562c, a length of the second oil supply inlet portion 1562a may
preferably be as short as possible.
[0203] The second oil supply connection portion 1562b may extend in
the axial direction from an end of the second oil supply inlet
portion 1562a and be recessed by an intermediate depth of the
orbiting end plate 151. Accordingly, oil flowing into the second
oil supply inlet portion 1562a may move toward the first oil supply
penetration portion 1562c through the second oil supply connection
portion 1561b.
[0204] The second oil supply penetration portion 1562c may be
formed through the inside of the orbiting end plate 151 in the
radial direction. Since the second oil supply penetration portion
1562c may be made in a direction from an outer circumferential
surface to an inner circumferential surface of the orbiting end
plate 151, a blocking bolt (not shown) may be coupled to an outer
end of the second oil supply penetration portion 1562c, so as to
seal the outer end of the second oil supply penetration portion
1562c.
[0205] The second pressure reducing member 1565a may be inserted
into the second oil supply penetration portion 1562c. The second
pressure reducing member 1565a may be configured as a pressure
reducing pin having an outer diameter smaller than an inner
diameter of the second oil supply penetration portion 1562c.
Accordingly, oil in the oil accommodating portion 155 may be
decompressed while passing through the second pressure reducing
member 1565a inside the second oil supply penetration portion 1562c
and then supplied to the second compression chamber V2.
[0206] The second oil supply outlet portion 1562d may penetrate
through the lower surface of the orbiting end plate 151 at an end
portion of the second oil supply penetration portion 1562c in the
radial direction. Accordingly, the second compression chamber oil
supply hole 1562 may allow the communication between the oil
accommodating portion 155 and the second compression chamber
V2.
[0207] The second oil supply outlet portion 1562d may be formed at
a position spaced apart from an inner circumferential surface of
the outermost orbiting wrap 152 by a preset interval. As described
above, the second oil supply outlet portion 1562d may penetrate
through a surface facing the fixed end plate 141, namely, the lower
surface of the orbiting end plate 151, near the outer end of the
first oil supply penetration portion 1562c. The second oil supply
outlet portion 1562d may have an inner diameter which is smaller
than or equal to an inner diameter of the second oil supply
penetration portion 1562c, for example, smaller than a wrap
thickness of the fixed wrap 144.
[0208] On the other hand, the first oil supply outlet portion 1561d
forming the outlet of the first compression chamber oil supply hole
1561 may be formed at a position where it communicates with the
first compression chamber V1, regardless of an orbiting position
(crank angle) of the orbiting scroll 150, and the second oil supply
outlet portion 1562d forming the outlet of the second compression
chamber oil supply hole 1562 may be formed at a position where it
communicates with the second compression chamber V2, regardless of
the orbiting position (crank angle) of the orbiting scroll 150.
[0209] FIG. 12 is a planar view illustrating an appropriate
position of an outlet of the first compression chamber oil supply
hole in FIG. 8. (a) of FIG. 12 illustrates the position of the
first compression chamber (pocket A) when the crank angle is
0.degree., and (b) of FIG. 12 illustrates the position of the first
compression chamber (pocket A) when the crank angle is 90.degree..
Also, (c) of FIG. 12 illustrates the position of the first
compression chamber (pocket A) when the crank angle is 180.degree..
In addition, (a+b+c) of FIG. 12 illustrates a portion where the
positions of the first compression chamber (pocket A) in (a), (b),
and (c) of FIG. 12 overlap. Hereinafter, an angle is a crank angle
unless otherwise specified.
[0210] Referring to (a) of FIG. 12, the first compression chamber
(pocket A) V1 may be shown at a time point when a compression
stroke starts just after completion of a suction stroke. In this
case, the first compression chamber (pocket A) V1 may be formed in
a crank angle range of approximately 0.degree. to 330.degree..
Therefore, considering only (a) of FIG. 12, it may be appropriate
that the outlet (first oil supply outlet portion) 1561d of the
first compression chamber oil supply hole 1561 is located within
the crank angle range V11 of approximately 0.degree. to
330.degree..
[0211] Referring to (b) of FIG. 12, the first compression chamber
(pocket A) V1 may be shown at a time point when the compression
stroke is in progress after moving along an orbiting trajectory of
the orbiting scroll 150. In this case, the first compression
chamber (pocket A) V1 may be formed in a crank angle range of
approximately 90.degree. to 420.degree.. Therefore, considering
only (b) of FIG. 12, it may be appropriate that the outlet (first
oil supply outlet portion) 1561d of the first compression chamber
oil supply hole 1561 is located within the crank angle range V12 of
approximately 90.degree. to 420.degree..
[0212] Referring to (c) of FIG. 12, the first compression chamber
(pocket A) V1 may be shown at a time point when the compression
stroke is further in progress after moving along the orbiting
trajectory of the orbiting scroll 150. In this case, the first
compression chamber (pocket A) V1 may be formed in a crank angle
range of approximately 180.degree. to 510.degree.. Therefore,
considering only (c) of FIG. 12, it may be appropriate that the
outlet (first oil supply outlet portion) 1561d of the first
compression chamber oil supply hole 1561 is located within the
crank angle range V13 of approximately 180.degree. to
510.degree..
[0213] However, when only one first compression chamber oil supply
hole 1561 is formed in the first compression chamber V1, the first
compression chamber oil supply hole 1561 may preferably be formed
to be included in the range of the first compression chamber V1 at
each crank angle exemplarily illustrated above. Accordingly, when
viewing (a+b+c) of FIG. 12, the first oil supply outlet portion
1561d as the outlet of the first compression chamber oil supply
hole 1561 may be formed in a section included in all cases where
the crank angle is 0.degree., 90.degree., and 180.degree., that is,
in a crank angle range V11+V12+V13 in which regions of the first
compression chamber at the respective crank angles overlap
together.
[0214] Accordingly, the first oil supply outlet portion 1561d
according to the implementation may be formed within a crank angle
range of approximately 180.degree. to 330.degree.. However,
considering the inner diameter of the first oil supply outlet
portion 1561d, the first oil supply outlet portion 1561d may
preferably be formed within a crank angle range of approximately
220.degree. to 290.degree..
[0215] On the other hand, FIG. 13 is a planar view illustrating an
appropriate position of an outlet of the second compression chamber
oil supply hole in FIG. 8. (a) of FIG. 13 illustrates the position
of the second compression chamber (pocket B) when the crank angle
is 180.degree., and (b) of FIG. 13 illustrates the position of the
second compression chamber (pocket B) when the crank angle is
260.degree.. Also, (c) of FIG. 13 illustrates the position of the
second compression chamber (pocket B) when the crank angle is
320.degree.. In addition, (a+b+c) of FIG. 13 illustrates a portion
where the positions of the second compression chamber (pocket B) in
(a), (b), and (c) of FIG. 13 overlap. Hereinafter, an angle is also
the crank angle unless otherwise specified.
[0216] Referring to (a) of FIG. 13, the second compression chamber
(pocket B) V2 may be shown at a time point when a compression
stroke starts just after completion of a suction stroke. In this
case, the second compression chamber (pocket B) V2 may be formed in
a crank angle range V21 of approximately -10.degree. to
320.degree.. Therefore, considering only (a) of FIG. 13, it may be
appropriate that the outlet (second oil supply outlet portion)
1562d of the second compression chamber oil supply hole 1562 is
located within the crank angle range of approximately -10.degree.
to 320.degree..
[0217] Referring to (b) of FIG. 13, the second compression chamber
(pocket B) V2 may be shown at a time point when the compression
stroke is in progress after moving along an orbiting trajectory of
the orbiting scroll 150. In this case, the second compression
chamber (pocket B) V2 may be formed in a crank angle range of
approximately 80.degree. to 40.degree.. Therefore, considering only
(b) of FIG. 13, it may be appropriate that the outlet (second oil
supply outlet portion) 1562d of the second compression chamber oil
supply hole 1562 is located within the crank angle range of
approximately 80.degree. to 400.degree..
[0218] Referring to (c) of FIG. 13, the second compression chamber
(pocket B) V2 may be shown at a time point when the compression
stroke is further in progress after moving along the orbiting
trajectory of the orbiting scroll 150. In this case, the second
compression chamber (pocket B) V2 may be formed in a crank angle
range V23 of approximately 170.degree. to 490.degree.. Therefore,
considering only (c) of FIG. 13, it may be appropriate that the
outlet (second oil supply outlet portion) 1562d of the second
compression chamber oil supply hole 1562 is located within the
crank angle range of approximately 170.degree. to 490.degree..
[0219] However, when only one second compression chamber oil supply
hole 1562 is formed in the second compression chamber V2, the
second compression chamber oil supply hole 1562 may preferably be
formed to be included in the range of the compression chamber at
each crank angle exemplarily illustrated above. Accordingly, when
viewing (a+b+c) of FIG. 13, the second oil supply outlet portion
1562d as the outlet of the second compression chamber oil supply
hole 1562 may be formed in a section included in all cases where
the crank angle is 180.degree., 260.degree., and 320.degree., that
is, in a crank angle range V21+V22+V23 in which regions of the
second compression chamber at the respective crank angles overlap
together.
[0220] Accordingly, the second oil supply outlet portion 1562d
according to the implementation may be formed within a crank angle
range of approximately 170.degree. to 330.degree.. However,
considering the inner diameter of the second oil supply outlet
portion 1562d, the second oil supply outlet portion 1562d may
preferably be formed within a crank angle range of approximately
210.degree. to 280.degree..
[0221] On the other hand, the position of the first oil supply
outlet portion 1561d and the position of the second oil supply
outlet portion 1562d may be linked to a design pressure ratio,
respectively.
[0222] That is, when the design pressure ratio is 1.0 to 1.1 (first
pressure ratio section), the first oil supply outlet portion 1561d
may be formed in the range of 0.degree. to 90.degree., and the
second oil supply outlet portion 1562d may be formed in the range
of 180.degree. to 260.degree..
[0223] In addition, when the design pressure ratio is 1.1 to 1.2
(second pressure ratio section), the first oil supply outlet
portion 1561d may be formed in the range of 90.degree. to
180.degree., and the second oil supply outlet portion 1562d may be
formed in the range of 260.degree. to 320.degree..
[0224] In addition, when the design pressure ratio is 1.2 to 1.3
(third pressure ratio section), the first oil supply outlet portion
1561d may be formed in the range of 180.degree. to 250.degree. and
the second oil supply outlet portion 1562d may be formed in the
range of 320.degree. to 380.degree..
[0225] On the other hand, the first oil supply outlet portion 1561d
may be formed at a position where the first compression chamber oil
supply hole 1561 communicates with the first compression chamber V1
and the second compression chamber oil supply hole 1562
communicates with the second compression chamber V2, independently,
regardless of the orbiting position (crank angle) of the orbiting
scroll 150.
[0226] FIG. 14 is a planar view, when viewing the orbiting scroll
from the bottom, for explaining appropriate spaced distances of the
first compression chamber oil supply hole and the second
compression chamber oil supply hole in FIG. 8 from the orbiting
wrap.
[0227] Referring to FIG. 14, the first oil supply outlet portion
1561d forming the outlet of the first compression chamber oil
supply hole 1561 may be formed at a position spaced apart from the
outer circumferential surface of the outermost orbiting wrap 152 by
a preset interval, and the second oil supply outlet portion 1562d
forming the outlet of the second compression chamber oil supply
hole 1562 may be formed at a position spaced apart from the inner
circumferential surface of the outermost orbiting wrap 152 by a
preset interval.
[0228] For example, when the position of the first oil supply
outlet portion 1561d is defined as a first oil supply position P1,
the position of the second oil supply outlet portion 1562d is
defined as a second oil supply position P2, a radial distance from
the outer circumferential surface of the outermost orbiting wrap
152 to the first oil supply position P1 is defined as a first
outlet distance L1, and a radial distance from the inner
circumferential surface of the outermost orbiting wrap 152 to the
second oil supply position P2 is defined as a second outlet
distance L2, the positions of the first oil supply outlet portion
1561d and the second oil supply outlet portion 1562d may be
calculated (determined or set), respectively.
[0229] That is, the position of the first oil supply outlet portion
1561d and the position of the second oil supply outlet portion
1562d according to the implementation may be determined such that
the first outlet distance L1 is greater than or equal to a value
obtained by subtracting the inner diameter d1 of the first oil
supply outlet portion 1561d from the wrap thickness t of the
orbiting wrap 152 and the second outlet distance L2 is greater than
or equal to a value obtained by subtracting the inner diameter d2
of the second oil supply outlet portion 1562d from the wrap
thickness t of the orbiting wrap 152. This may be expressed by the
following relation:
{Wrap thickness-Oil supply outlet portion.ltoreq.Position of Oil
supply outlet portion}
[0230] In other words, the first oil supply outlet portion 1561d
according to the implementation may be formed at a position spaced
apart from the outer circumferential surface of the outermost
orbiting wrap 152 by the inner diameter d1 of the first oil supply
outlet portion 1561d or farther, and the second oil supply outlet
portion 1562d according to the implementation may be formed at a
position spaced apart from the inner circumferential surface of the
outermost orbiting wrap 152 by the inner diameter d2 of the second
oil supply outlet portion 1562d or farther.
[0231] Here, the first outlet distance L1 may be greater than or
equal to the second outlet distance L2. This will be described in
detail later with reference to FIG. 15.
[0232] Accordingly, when the orbiting scroll 150 performs the
orbiting motion relative to the fixed scroll 140, the first
compression chamber oil supply hole 1561 (precisely, the first oil
supply outlet portion) may almost communicate only with the first
compression chamber V1 and the second compression chamber oil
supply hole 1562 (precisely, the second oil supply outlet portion)
may almost communicate only with the second compression chamber
V2.
[0233] FIG. 15 is a schematic view illustrating open sections of
the respective compression chamber oil supply holes according to
positions of the first compression chamber oil supply hole and the
second compression chamber oil supply hole in accordance with an
implementation of the present disclosure. (a) of FIG. 15
illustrates implementations in which the position of the first oil
supply outlet portion is divided into three stages and the position
of the second oil supply outlet portion is divided into two stages.
(b) of FIG. 15 shows graphs that analyze an oil supply section of
each compression chamber based on a crank angle in the case of the
division shown in (a) of FIG. 15.
[0234] As illustrated in (a) and (b) of FIG. 15, when the first oil
supply outlet portion 1561d is formed at a position {circle around
(1)} adjacent to an outer circumferential surface 152a of the
orbiting wrap 152 and the second oil supply outlet portion 1562d is
formed at a position {circle around (1)}' adjacent to an inner
circumferential surface 152b of the orbiting wrap 152, a first oil
supply section in which the first oil supply outlet portion 1561d
communicates with the first compression chamber V1 corresponds to a
section in a crank angle range of approximately -100.degree. to
190.degree. and a second oil supply section in which the second oil
supply outlet portion 1562d communicates with the second
compression chamber V2 corresponds to a section in a crank angle
range of approximately 70.degree. to 350.degree.. [See a top graph
in (b) of FIG. 15]
[0235] Accordingly, a section in which the first oil supply section
As1 and the second oil supply section As2 overlap each other, that
is, a section in which the first compression chamber V1 and the
second compression chamber V2 communicate with each other
corresponds to approximately 70.degree. to 190.degree. (first
overlap section) Ao1 and to approximately 250.degree. to
350.degree. (second overlap section) Ao2. These first overlap
section Ao1 and second overlap section Ao2 are slashed in (b) of
FIG. 15.
[0236] In these overlap sections Ao1 and Ao2, the first compression
chamber V1 and the second compression chamber V2 may communicate
with each other through the first compression chamber oil supply
hole 1561 and the second compression chamber oil supply hole 1562.
Then, a back flow of refrigerant from the first compression chamber
V1 to the second compression chamber V2 may occur in the first
overlap section Ao1 and a back flow of refrigerant from the second
compression chamber V2 to the first compression chamber V1 may
occur in the second overlap section Ao2, due to a pressure
difference between the first and second compression chambers V1 and
V2.
[0237] Referring back to (a) and (b) of FIG. 15, when the first oil
supply outlet portion 1561d is formed at a position {circle around
(2)} farther spaced apart from the outer circumferential surface
152a of the orbiting wrap 152 and the second oil supply outlet
portion 1562d is formed at a position {circle around (2)}' farther
spaced apart from the inner circumferential surface 152b of the
orbiting wrap 152, the first oil supply section As1 in which the
first oil supply outlet portion 1561d communicates with the first
compression chamber V1 corresponds to a section in a crank angle
range of approximately -40.degree. to 140.degree. and the second
oil supply section As2 in which the second oil supply outlet
portion 1562d communicates with the second compression chamber V2
corresponds to a section in a crank angle range of 90.degree. to
330.degree.. [See a middle graph of (b) of FIG. 15]
[0238] Accordingly, a section in which the first oil supply section
As1 of the first compression chamber V1 and the second oil supply
section V2 of the second compression chamber V2 overlap each other,
that is, a section in which the first compression chamber V1 and
the second compression chamber V2 communicate with each other
corresponds to approximately 90.degree. to 140.degree. (overlap
section) Ao1 and to approximately 320.degree. to 330.degree.
(overlap section) Ao1. These overlap sections Ao1 and Ao2 are
slashed in (b) of FIG. 15.
[0239] In these overlap sections Ao1 and Ao2, as aforementioned,
the first compression chamber V1 and the second compression chamber
V2 may communicate with each other through the first compression
chamber oil supply hole 1561 and the second compression chamber oil
supply hole 1562. Then, a back flow of refrigerant from the first
compression chamber V1 to the second compression chamber V2 may
occur in the overlap sections Ao1 and Ao2 due to a pressure
difference between the first and second compression chambers V1 and
V2.
[0240] However, in this case, as described above, the overlap
sections Ao1 and Ao2 may be shortened, compared to those formed
when the first oil supply outlet portion 1561d and the second oil
supply outlet portion 1562d are disposed adjacent to the side
surface of the orbiting wrap 152, thereby reducing leakage between
the compression chambers by that much.
[0241] Referring back to (a) and (b) of FIG. 15, when the first oil
supply outlet portion 1561d is formed at a position {circle around
(3)} farthest spaced apart from the outer circumferential surface
152a of the orbiting wrap 152 and the second oil supply outlet
portion 1562d is formed at a position {circle around (3)}' farther
spaced apart from the inner circumferential surface 152b of the
orbiting wrap 152, the first oil supply section As1 in which the
first oil supply outlet portion 1561d communicates with the first
compression chamber V1 corresponds to a section in a crank angle
range of approximately 0.degree. to 90.degree. and the second oil
supply section As2 in which the second oil supply outlet portion
1562d communicates with the second compression chamber V2
corresponds to a section in a crank angle range of 90.degree. to
330.degree..
[0242] Here, the position of {circle around (3)}' is the same as
that the position {circle around (2)}'. Therefore, the distance
(the first outlet distance L1) from the outer circumferential
surface of the orbiting wrap 152 to the first oil supply outlet
portion 1561 may be longer than the distance (the second outlet
distance L2) from the inner circumferential surface of the orbiting
wrap 152 to the second oil supply outlet portion 1562. [See a
bottom graph of (b) of FIG. 15]
[0243] Accordingly, a section in which the first oil supply section
As1 of the first compression chamber V1 and the second oil supply
section As2 of the second compression chamber V2 overlap each
other, that is, an overlap section in which the first compression
chamber V1 and the second compression chamber V2 communicate with
each other may hardly occur.
[0244] This may allow oil to be smoothly supplied to the first
compression chamber V1 and the second compression chamber V2, so as
to reduce friction loss in the compression unit and prevent leakage
between the compression chambers through the first compression
chamber oil supply hole 1561 and the second compression chamber oil
supply hole 1562. This may result in enhancing compression
efficiency.
[0245] In addition, a non-oil supply section As3 may be formed
between the start of the first oil supply section As1 and the end
of the second oil supply section As2 based on the crank angle. That
is, as illustrated in (b) of FIG. 15, the non-oil supply section
As3, in which oil is not supplied because the first oil supply
outlet portion 1561d and the second oil supply outlet portion 1562d
are blocked, may be formed between the start of the first oil
supply section As1 and the end of the second oil supply section
As2. This non-oil supply section As3 may be formed to be greater
than 0.degree. and smaller than or equal to 30.degree.. In this
way, the non-oil supply section in which oil is not supplied to the
compression chambers V1 and V2 can be minimized so as to reduce
friction loss as much as possible.
[0246] On the other hand, the foregoing implementation illustrates
the oil supply structure in the scroll compressor having the
suction passage opening and closing valve disposed in the suction
passage. However, in some cases, the oil supply structure may also
be equally applied to a scroll compressor in which the suction
passage opening and closing valve is not disposed in the suction
passage.
[0247] FIG. 16 is a longitudinal sectional view illustrating
another implementation of a scroll compressor, to which the
compression chamber oil supply holes according to the present
disclosure are applied.
[0248] Referring to FIG. 16, a basic structure of a scroll
compressor according to this implementation is the same as that of
the foregoing implementation illustrated in FIG. 2, and thus a
description thereof will be replaced with the description of the
foregoing implementation.
[0249] For example, in the scroll compressor according to this
implementation, the first compression chamber oil supply hole 1561
and the second compression chamber oil supply hole 1562 may be
provided to communicate with the first compression chamber V1 and
the second compression chamber V2, respectively.
[0250] The first compression chamber oil supply hole 1561 and the
second compression chamber oil supply hole 1562 may be formed in
the same manner as in the foregoing implementation. Specifically,
the oil supply section of the first oil supply outlet portion 1561d
forming the outlet of the first compression chamber oil supply hole
1561 and the second oil supply outlet portion 1562d forming the
outlet of the second compression chamber oil supply hole 1562 may
not overlap each other. The positions of the first oil supply
outlet portion 1561d and the second oil supply outlet portion 1562d
are the same as those of the foregoing implementation.
[0251] Accordingly, the first compression chamber V1 and the second
compression chamber V2 can be prevented from communicating with
each other through the first compression chamber oil supply hole
1561 and the second compression chamber oil supply hole 1562,
thereby suppressing refrigerant from leaking between the
compression chambers in advance.
[0252] However, in this implementation, the refrigerant suction
pipe 115 may be inserted through the casing 110 and communicate
with the suction chamber Vs through the fixed scroll 140 in the
radial direction. In this case, a separate suction passage opening
and closing valve may not be installed between the refrigerant
suction pipe and the suction chamber, and in some cases, may
alternatively be installed.
[0253] Meanwhile, although not shown in the drawings, the first
compression chamber oil supply hole and the second compression
chamber oil supply hole may be equally applied to a so-called
top-compression type scroll compressor in which a compression unit
is located above a motor unit. A description of this will be
replaced by the description of the foregoing implementations.
* * * * *